Fluid processing system and method

ABSTRACT

This disclosure relates to a centrifugal vortex system for preparing a liquid, such as fuel and includes a chamber housing defining a vortex chamber. An array of tangential apertures are formed in the chamber housing to permit fluid to be turbulently introduced into the vortex chamber to create a vortical flow of fluid through the vortex chamber. In one embodiment, a plurality of vortex chambers are arranged in series to allow the fluid to pass through several vortex chambers. In other embodiments, the chamber housing may be stepped, textured, or both to increase the turbulence of the flow through the chamber. In yet another embodiment, a pressure differential supply jacket is provided to normalize the amount of flow through the tangential apertures according to the location of the apertures. A centrifuge chamber is also disclosed which has a plurality of output conduits on a bottom surface and a tapered extension member downwardly extending from a top surface to enhance the centrifugal flow of the fluid. Additionally, a bypass conduit is provided to selectively permit the flow to bypass one or more chambers.

TECHNICAL FIELD

[0001] This invention relates to fluid vaporizing and homogenizingdevices, to systems for vaporizing and homogenizing fluids, and moreparticularly to devices and systems for producing finely homogenized orvaporized gas-phase fluid mixtures.

BACKGROUND OF THE INVENTION

[0002] Many types of devices have been developed over the years for thepurpose of converting liquids or aerosols into gas-phase fluids. Manysuch devices have been developed to prepare fuel for use in internalcombustion engines. To optimize fuel oxidation within an engine'scombustion chamber, the fuel/air mixture commonly must be furthervaporized or homogenized to achieve a chemically-stoichiometricgas-phase mixture. Ideal fuel oxidation results in more completecombustion and lower pollution.

[0003] More specifically, relative to internal combustion engines,stoichiometricity is a condition where the amount of oxygen required tocompletely burn a given amount of fuel is supplied in a homogeneousmixture resulting in optimally correct combustion with no residuesremaining from incomplete or inefficient oxidation. Ideally, the fuelshould be completely vaporized, intermixed with air, and homogenizedprior to entering the combustion chamber for proper oxidation.Non-vaporized fuel droplets generally do not ignite and combustcompletely in conventional internal and external combustion engines,which presents problems relating to fuel efficiency and pollution.

[0004] Incomplete or inefficient oxidation of fuel causes exhaustion ofresidues from the internal or external combustion engine as pollutants,such as unburned hydrocarbons, carbon monoxide, and aldehydes, withaccompanying production of oxides of nitrogen. To meet emissionstandards, these residues must be dealt with, typically requiringfurther treatment in a catalytic converter or a scrubber. Such treatmentof these residues results in additional fuel costs to operate thecatalytic converter or scrubber. Accordingly, any reduction in residuesresulting from incomplete combustion would be economically andenvironmentally beneficial.

[0005] Aside from the problems discussed above, a fuel-air mixture thatis not completely vaporized and chemically stoichiometric causes thecombustion engine to perform inefficiently. Since a smaller portion ofthe fuel's chemical energy is converted to mechanical energy, fuelenergy is wasted thereby generating unnecessary heat and pollution.Thus, by further breaking down and more completely vaporizing thefuel-air mixture, higher engine efficiency may be obtained.

[0006] Attempts have been made to alleviate the above-described problemswith respect to fuel vaporizaton and incomplete fuel combustion. Forexample, U.S. Pat. No. 4,515,734, U.S. Pat. No. 4,568,500, U.S. Pat. No.5,512,216, U.S. Pat. No. 5,472,645, and U.S. Pat. No. 5,672,187 disclosevarious devices which vaporize fuel as it is being provided to theintake manifold of an engine. These prior devices generally involve aseries of mixing sites and a venturi for vaporizing fuel and air.

[0007] It should be noted that the above-mentioned prior devices providecertain advantages in the operation of a combustion engine by allowing arelatively high degree of hydrocarbon burning in an associated engine.Nevertheless, there are certain problems with these prior devices.

[0008] First, the apertures for inputting air into the vortex chambersare arranged in a single column of three apertures. This manner ofintroducing air into the vortex chambers may cause the fluid within thevortex chamber to separate into discrete rings of fluid along the innerwall of the vortex chamber. Typically, one such ring will be associatedwith one of the apertures. The tendency for fluids to collect in ringsalong the vortex chamber walls necessarily limits the degree ofturbulence (and thus the efficiency of vaporization) within a givenvortex chamber.

[0009] Additionally, prior devices have employed vortex chambers thathave smooth, cylindrical inner walls. A smooth vortex chamber inner wallconstruction may limit the degree of turbulence within a given chamberand the effective rate of vaporization within the vortex chambers.

[0010] Another perceived shortcoming of prior devices is their inabilityto compensate for differential pressures at the various inlets leadingto the vortex chamber. As the air/fuel mixture passes through thevarious vortex chambers, additional air is tangentially added in eachchamber which causes a pressure differential at the various inlets. Bysupplying ambient air at all of these inlets to the vortex chamber, ithas been difficult to maintain an optimal air-to-fuel ratio of theair/fuel mixture as the mixture passes through the vortex chambers.

[0011] Yet another aspect of the pressure differential problemassociated with prior known devices is that there is a tendency for thevortex chambers positioned closer to the low pressure end of the flowpath (closer to the engine manifold) to dominate the other vortexchambers by receiving substantially more flow. This tendency isparticularly noticeable and problematic during periods of engineacceleration. As the vortex chambers closer to low pressure end of theflow path dominate the other vortex chambers, the effectiveness of theother vortex chambers is significantly reduced.

[0012] The prior centrifuge vaporization devices also have certainlimitations, such as being too voluminous, failing to effectivelyintroduce fluid into the centrifuge chamber tangentially, unnecessarilyinhibiting the drawing power of the engine manifold vacuum, and unevenlydischarging the centrifuge contents into the engine manifold.

[0013] An additional limitation of prior centrifuge vaporization deviceshas been their failure to adequately mix ambient air with fuel prior toadding the air and fuel into the vortex chamber. Absent adequateair/fuel premixing, excessive hydrocarbons are produced. Prior attemptsto solve this problem have proven ineffective in that, even if fuel in agaseous or aerosol state is sprayed into an air flow stream, the fuelsubsequently liquefies prior to entering into the vortex chamber, thusnullifying any advantage obtained by spraying a gaseous or aerosol fuelinto an air stream.

[0014] A further problem of prior centrifuge vaporization devices hasbeen their failure to provide a venturi configuration which is largeenough to attain volumetric efficiencies at high RPM's, yet small enoughto get high resolution responses at lower RPM's. Indeed, the priordevices have generally had to choose between volumetric efficiency athigh RPM's and high resolution response at lower RPM's. A need exists,therefore, for a centrifuge vaporization device which can attainvolumetric efficiency at high RPM's and high resolution response atlower RPM's.

[0015] Yet another problem concerning prior cyclone vaporization devicesis that they have failed to appreciate or utilize the advantagesassociated with adjustable vortex chamber output ports and adjacentchambers of different diameters.

[0016] Another problem, different from applications of vortex technologyto internal combustion engines, relates to the extreme vaporizationneeded for various medications administered via inhalers. An inhalertypically produces a liquid/gas mixture of the medication for inhalingdirectly into the lungs. Problems have arisen, however, in that the highdegree of vaporization required for directly passing the medicationthrough the lungs into the bloodstream has been difficult to achieve.That is, excess amounts of the medication remain liquefied, rather thanbeing further broken down into smaller molecular size particles, forpassing immediately through the lungs into the bloodstream. A needexists, therefore, to develop certain vaporization devices that willfurther vaporize and homogenize liquid/gas mixtures into a vapor ofsufficiently small vapor particles for administering medication directlyinto the bloodstream via the lungs.

[0017] Still another need exists with respect to utilization of abreakdown process for incineration and waste management. To the extentwaste fluid particles can be broken down into extremely small particlesizes, a mixture being introduced into a waste disposal or wastetreatment device will create a more efficient burn, thereby minimizingpollution and increasing the efficiency by which waste fluids areincinerated.

[0018] In view of the foregoing, there is a need to develop acentrifugal vortex system that solves or substantially alleviates theabove-discussed limitations associated with known prior devices. Thereis a need to develop a centrifugal vortex system with a vortex chamberthat enables a more optimal turbulent flow, that more completely breaksdown liquid into smaller sized particles of vapor fluid, and thatnormalizes the flow through the various apertures formed in the vortexchamber housing. There is a further need to provide a centrifugal vortexsystem that more optimally premixes air and fuel prior to introducingthe air/fuel mixture into the vortex chamber. Another need exists toprovide a low-volume centrifuge apparatus that more optimally mixes,vaporizes, homogenizes, and discharges more minutely sized molecularvapor particles into an engine manifold, from an inhaler-type medicinaladministration device, and to/from other desired applications.

SUMMARY AND OBJECTS OF THE INVENTION

[0019] It is an object of the invention to provide a vortex chamber thatenables a more optimal turbulent flow and which substantially eliminatesthe formation of liquid orbital rings on the inner walls within thevortex chamber.

[0020] Another object of the invention is to provide a plurality ofvortex chambers with air being introduced only in the first chamber tomaintain a constant air/fuel ratio of the air/fuel mixture as themixture advances through subsequent chambers.

[0021] Another object of the invention is to provide a vortex chamberhousing with a stepped inner wall surface for increasing the turbulenceof fluid flowing through the vortex chamber.

[0022] Another object of the invention is to provide a vortex chamberhousing with an irregular or textured inner wall surface for increasingthe turbulence of fluid flowing through the vortex chamber.

[0023] Another object of the invention is to provide a pressuredifferential supply, such as a tapered air-feed channel formed perhapsby a jacket, to equalize the amount of flow entering several inputapertures formed in a vortex chamber.

[0024] Another object of the invention is to provide a series oftangentially oriented baffles associated with a centrifuge chamber toform a series of tangential passageways into the centrifuge chamber toenhance the centrifugal flow of fluid in the centrifuge chamber.

[0025] Another object of the invention is to provide a movable conduitwhich is capable of being inserted through a series of vortex chambersto selectively isolate and bypass one or more of the other chambers.

[0026] Another object of the invention is to provide a vortex chamberwith an adjustable output port to assist in regulating the flow of fluidthrough the output port.

[0027] Another object of the invention is to provide a centrifugechamber with a plurality of output ports to homogenize and furthervaporize the fluid output flow to the engine.

[0028] Another object of the invention is to provide a tapered extensionon a top surface of the centrifuge chamber to reduce the chamber volumeand to enhance the centrifugal or vortical flow of fluid within thechamber.

[0029] Another object of the invention is to increase turbulence withinthe vortex chamber by reducing the chamber volume and by employing acentrifuge vertical wall with a height less than the maximum insidediameter of an associated venturi.

[0030] Another object of the invention is to provide a series ofincreasing diameter vortex chambers to normalize or equalize the fluidflow in the respective vortex chambers.

[0031] Another object of the invention is to provide a venturi and anassociated centrifuge chamber where the ratio of the venturi throatdiameter to the diameter of the centrifuge output port is approximately1:1.66.

[0032] Another object of the invention is to provide a preliminarymixing chamber to premix the air and the fuel prior to introducing theair/fuel mixture into a vortex chamber for homogenization andvaporization.

[0033] Another object of the invention is to provide a more optimalturbulence within a vortex chamber and to achieve improved vaporizationby causing a vortical flow to spin in alternative, opposite spindirections as the vortical flow passes from one vortex chamber to anadjacent vortex chamber.

[0034] Another object of the present invention is to provide acentrifuge vaporization device which can attain a high volumetricefficiency at high RPM's and high resolution response at lower RPM's.

[0035] Still another object of the present invention is to provide adevice for breaking down a vapor/gaseous mixture into more minute sizedparticles on a molecular scale for medical applications.

[0036] Still another object of the invention is to produce a device thatallows a vapor/liquid mixture to be broken down into extremely smallsized particles such that the particles pass immediately and directlythrough the lungs into a person's bloodstream.

[0037] Yet another object of the present invention is to provide adevice that breaks down a flow of fluid comprising liquid and vaporparticles such that the fluid flow will burn more optimally in anincinerator.

[0038] Still another object of the invention is to provide a device thatallows fuel to be homogenized to a degree where a more optimalcombustion is achieved thereby reducing pollutants created from thecombustion process.

[0039] Another object of the invention is to provide a device with anextension arm within a centrifuge housing to prevent a blackflow offluid out of the centrifuge housing and to enhance the centrifugal flowof fluid in the centrifuge housing.

[0040] The foregoing objects are achieved by a centrifugal vortex systemthat enhances the turbulent flow and the vaporization of a fluid in avortex chamber by a particular premixing process that combines air andfuel prior to introducing the air/fuel mixture into an array ofapertures formed in a vortex chamber housing. The apertures are formedin the vortex chamber housing to cause the air/fuel mixture to beintroduced tangentially into the vortex chamber. The flow into thevarious apertures is equalized by a differential supply configurationthat enables effective use of all apertures.

[0041] In one embodiment, the inner wall of the vortex chamber housingis stepped or textured, or both, to enhance the turbulence of a flowthrough the vortex chamber. In another embodiment, the centrifugechamber has a series of baffles and a tapered extension to enhance thecentrifugal flow of fluid in the vortex chamber. In yet anotherembodiment, an elongated conduit is insertable through a series ofvortex chambers to selectively isolate and/or bypass one or more of thechambers. In still another embodiment, the vortex chamber output has anadjustable diameter for regulating the flow through the vortex chamber.

[0042] Other objects, features, and advantages of the invention willbecome apparent from the following detailed description of the inventionwith reference to the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

[0043] Preferred embodiments of the invention are described below withreference to the accompanying drawings:

[0044]FIG. 1 is a top sectional view of a centrifugal vortex systemaccording to the present invention;

[0045]FIG. 2 is a side sectional view taken along line 2-2 of FIG. 1, ofthe centrifugal vortex system;

[0046]FIG. 3 is an enlarged breakaway sectional view of a portion of thevaporizing section of FIG. 1;

[0047]FIG. 4 is a top view of the injector plate of FIG. 1;

[0048]FIG. 5 is a sectional view taken along line 5-5 of FIG. 4 of theinjector plate;

[0049]FIG. 6 is a bottom view of the injector plate of FIG. 1;

[0050]FIG. 7 is a sectional side view of an alternative embodiment of avortex configuration according to the present invention;

[0051]FIG. 8 is a bottom sectional view taken along line 8-8 of FIG. 7of the differential inlet supply configuration to a vortex chamberassembly;

[0052]FIG. 9 is a side sectional view taken along line 9-9 of FIG. 8 ofthe differential inlet supply configuration to a vortex housingassembly;

[0053]FIG. 10 is a top view of the differential inlet supplyconfiguration to a vortex housing assembly of FIG. 8;

[0054]FIG. 11 is a bottom sectional view of an alternative embodiment ofa differential inlet supply configuration to a vortex chamber assemblyaccording to the present invention;

[0055]FIG. 12 is a side sectional view, taken along line 12-12 of FIG.11, of the differential inlet supply configuration to a vortex chamberassembly;

[0056]FIG. 13 is a top view of the differential inlet supplyconfiguration for the vortex chamber assembly of FIG. 11;

[0057]FIG. 14 is a perspective view of an alternative embodiment of avortex chamber housing according to the present invention;

[0058]FIG. 15 is a top partial sectional view of another alternativeembodiment of a centrifugal vortex system according to the presentinvention;

[0059]FIG. 16 is an enlarged sectional view of the elongated conduitassembly shown in FIG. 15;

[0060]FIG. 17 is an enlarged view of the elongated conduit assemblyshown in FIG. 15 with the elongated conduit retracted from the vortexchambers;

[0061]FIG. 18 is a sectional view of yet another alternative embodimentof a vortex housing according to the present invention;

[0062]FIG. 19 is a sectional view of still another alternativeembodiment of a vortex chamber housing according to the presentinvention;

[0063]FIG. 20 is a partial sectional view of an adjustablecross-sectional area output port mechanism according to the presentinvention;

[0064]FIG. 21 is a top sectional view of an alternative embodiment of acentrifugal vortex system according to the present invention;

[0065]FIG. 22 is a top sectional view of yet another alternativeembodiment of a centrifugal vortex system according to the presentinvention; and

[0066]FIG. 23 is a perspective view of yet another alternativeembodiment of a vortex chamber housing according to the presentinvention;

[0067]FIG. 24 is a sectional side elevation view of an alternativeembodiment of a venturi according to the present invention;

[0068]FIG. 25 is a partial cross-sectional view, taken along the line25-25 of FIG. 24, of an alternate embodiment of a venturi according tothe present invention;

[0069]FIG. 26 is a plan view of still another alternate embodiment of acentrifugal vortex system according to the present invention,

[0070]FIG. 27 is a partial sectional side elevation view, taken alongthe line 27-27 of FIG. 26, of the centrifugal vortex system of thepresent invention;

[0071]FIG. 28 is a partial sectional side elevation view of thecentrifugal vortex system shown in FIG. 26;

[0072]FIG. 29 is a partial sectional view, taken along the line 29-29 ofFIG. 28, of the centrifugal vortex system according to the presentinvention;

[0073]FIG. 30 is an enlarged view of the linkage assembly illustrated inFIG. 29;

[0074]FIG. 31 is a sectional side elevation view of yet anotheralternate embodiment of a centrifugal vortex system according to thepresent invention;

[0075]FIG. 32 is a sectional side elevation view of still anotheralternate embodiment of a centrifugal vortex system for vaporizing afluid according to the present invention; and

[0076]FIG. 33 is an enlarged sectional view of a portion of theembodiment illustrated in FIG. 32.

DETAILED DESCRIPTION OF THE INVENTION

[0077] In the context of this document, the terms “homogenize” or“vaporize” or any derivative of these terms means to convert a liquidfrom an aerosol or vapor-phase to a gas-phase by vorticular turbulencewhere high velocity, low pressure, and high vacuum conditions exist,i.e., where differential pressures exist.

[0078] FIGS. 1-6 show a first embodiment of a centrifugal vortex system30 according to the present invention. As shown in FIG. 1, thecentrifugal vortex system 30 has three sections: a fuel vaporizingsection 32, a main air section 34, and a centrifuge section 36. The fuelvaporizing section 32 is illustrated as having two fuel injectors 38mounted in bores 40 formed in an injector plate 42. The fuel injectors38 may comprise conventional electronic fuel injectors and preferablyhave a spray angle of about 30°.

[0079] A preliminary mixing chamber 44 is formed in the fuel vaporizingsection 32, into which fuel is sprayed by the output ports 46 of thefuel injectors 38. Ambient air is also introduced into the preliminarymixing chamber 44 through an ambient air conduit 50 and is to be mixedwith fuel sprayed by the fuel injectors 38. The preliminary mixingchamber 44 is defined in part by an exterior surface 52 of a vortexchamber housing 54 and the exterior surface 68 of a tapered extension58. The preliminary mixing chamber 44 is further defined by the interiorsurface 56 of a pressure differential supply jacket 60. The purpose andfunction of the jacket 60 and the vortex chamber housing 54 arediscussed in more detail below.

[0080] The vortex chamber housing 54 comprises the exterior surface 52,an inner chamber wall surface 62, and a bottom surface 63. Additionally,the vortex chamber housing 54 includes the tapered extension 58 toenhance the flow of fluid in the preliminary mixing chamber 44, and isto be secured to the injector plate 42 by set screw 48 (FIG. 3) insertedthrough bore 49. The vortex chamber inner chamber wall surface 62defines a vortex chamber 64 in which a vortical flow of fluid iscreated. The vortex chamber housing 54 has an array of apertures 66journalled into the housing at an angle to allow the input of fluid,such as an air/fuel mixture, tangentially into the vortex chamber 64. Avortex chamber top edge 61 abuts a jacket top inside surface 55.Advantageously, a conventional gasket (not shown) may be interposedbetween the edge 61 and the top surface 55 to prevent fluid from leakinginto the vortex chamber 64 between the edge 61 and the surface 55.

[0081] As shown in FIG. 3, the array of apertures 66 are arranged in aplurality of rows R and in a plurality of columns C about the vortexchamber 64 to enhance the turbulence of the vortical flow through thechamber 64. Preferably, the rows R and the columns C arecircumferentially staggered or offset relative to each other. Byorienting the array of apertures 66 in staggered rows and columns, thetendency for the fluid within the vortex chamber 64 to separate intodiscrete orbital rings is eliminated or at least substantiallyalleviated. Additionally, this aperture orientation significantlyenhances the degree of turbulence (and thus the efficiency ofvaporization) within a given vortex chamber.

[0082] A pressure differential supply configuration is formed by atapered jacket 60 positioned around the vortex chamber housing 54. Asshown, the jacket 60 includes a variable thickness portion 75 whichprovides an increasing diameter to the tapered inside surface 56. Thejacket 60 terminates at edge 57. The jacket 60 also includes an outputport 70 through which fluid flows after being processed in the vortexchamber 64. The output port 70 is defined by a cylindrical surface 71which intersects the jacket top surface 55 at rounded corner 73. Thediameter of the jacket interior surface 56 is illustrated as beingsmallest at the end closest to the jacket output port 70. The diameterof the jacket interior surface 56 gradually increases from that pointtoward the edge 57. While the variable diameter surface is illustratedas generally comprising the tapered inside surface 56, it is appreciatedthat a stepped inside surface may also be effectively employed.

[0083] The variable diameter jacket interior surface 56, when positionedaround the vortex chamber housing 54, defines a variable width gap 72between the jacket interior surface 56 and the vortex chamber housingexterior surface 52. As shown in FIG. 3, the variable width gap has asmaller width at d₁ and a larger width at d₂. The variable width gap 72creates a variable pressure differential across the apertures 66 formedin the vortex chamber housing 54 and restricts the flow through theapertures 66 closer to the port 70 more than the apertures 66 locatedfarther from the port 70. Thus, a differential pressure of fluid isprovided at the various input apertures 66 according to the location ofthe apertures relative to the jacket output port 70. In operation, theapertures 66 closest to output port 70 will be provided with morepressure because this end comprises the lower pressure end of the fuelvaporizing section 32.

[0084] By positioning a variable pressure supply configuration, such asthe jacket 60, around the apertures 66 formed in the chamber housing 54,the amount of fluid flow entering the various apertures 66 issubstantially equalized. Having a substantially equalized flow of fluidthrough the various apertures 66 enhances the efficiency andeffectiveness of the vortex chamber 64.

[0085] The jacket 60 and the vortex chamber housing 54 are illustratedin FIG. 1 as being mounted within a fuel vaporizing housing 74 having aninterior surface 76. Specifically, a top outside surface 79 (FIG. 3) ofthe jacket 60 is positioned adjacent to a top inside surface 77 of thehousing 74. The ambient air conduit 50, discussed above, is defined bythe fuel vaporizing housing interior surface 76 and the exterior surface68 of the tapered extension 58.

[0086] The injector plate 42 is shown in FIGS. 1, 3, 4, 5, and 6. Theinjector plate 42 includes a pair of bores 40 formed through the bottomsurface 47 to receive the fuel injectors 38 (FIG. 1). The injector plate42 further includes a first shoulder 39 and a second shoulder 41 (FIGS.4 and 5). The first shoulder 39 abuts a connecting member 43 and thesecond shoulder 41 abuts the jacket edge 57 (FIG. 1). A cylindricalcenter extension 45 abuts and is connected to the tapered extension 58(FIG. 1) via the set screw 48.

[0087] The main air section 34, as illustrated in FIGS. 1 and 2,comprises a main air housing 80, a venturi body 82, and a conventionalbutterfly throttle plate 84. An air intake opening 86 is positioned atone end of the main air section 34. The air intake opening 86 leads toan interior cylindrical portion 90 having an annular inside surface 92.

[0088] The conventional throttle plate 84 is pivotally secured withinthe interior cylindrical portion 90. The throttle plate 84 is secured toa rotatable central shaft 96, which is oriented transverse to thedirection of air flow F through the hollow interior 90. Rotation of theshaft 96 will adjust an inclination angle of the throttle plate 84within the hollow interior 90, thereby changing the volume of air andthus the air/fuel mixture admitted to the engine.

[0089] An ambient air channel 100 is formed in the main air intakehousing 80. The air channel 100 is in fluid communication with a slot 94formed in the main air intake housing 80. Sequential ambient airconduits 102 and 50 allow air to pass through the channel 100 and theslot 94 into the preliminary mixing chamber 44.

[0090] A venturi 82 is mounted within the main air section 34 andcomprises an input 104, a plurality of elongated apertures 106, and aventuri output 110. Additionally, the venturi 82 includes a venturiexterior surface 112 and a venturi interior surface 114. As shown, thediameter of the venturi interior surface 114 is maximized at the venturiinput 104 and at the venturi output 110. The diameter of the venturiinterior surface 114 is approximately the same at the venturi input 104and at the venturi output 110. In contrast, the diameter of the venturiinterior surface 114 is minimized at the venturi throat 116. An annularstep is formed on the venturi interior surface 114 adjacent to theventuri throat 116.

[0091] The main air intake section 34 also includes a transverse annularedge 122 (FIGS. 1 and 2) which intersects the annular inside surface 92at an annular outside corner 124. The edge 122 also intersects anannular surface 126 at an annular inside corner 130. The annular surface126 also intersects with a transverse edge 132 at an annular corner 134.The venturi 82 is positioned within the main air section adjacent to theannular surface 126 by securing the exterior surface 112 of the venturi82 to the annular surface 126 by adhesion, by an interference fit, or byany other conventional manner.

[0092] An intermediate mixing chamber 136 (FIG. 1) is formed in the mainair intake section 34 to cause a spinning column of fluid exiting thejacket output port 70 to enfold and to mix turbulently prior to enteringthe venturi 82 through the elongated apertures 106. The intermediatemixing chamber 136 serves to further vaporize and homogenize the fluid.The intermediate mixing chamber is defined by the annular surface 126and the transverse annular surface 140 which intersect at corner 142.The centrifuge section 36 is attached to the main air section 34 at thetransverse edge 132.

[0093] Fluid discharged from the venturi output 110 passes into thecentrifuge section 36 through an intake opening 144. The centrifugesection 36 generally comprises a centrifuge housing 142, the intakeopening 144, an entry chamber 146, a series of baffles 150 orientedtangentially relative to a centrifuge chamber 152, and a plurality ofoutput passageways 154. As shown, the centrifuge housing is a generallycylindrical configuration comprising an annular vertically directed wallsurface 156 which is interrupted by the intake opening 144. The wallsurface 156 is formed integrally with a top wall 160 (FIG. 2).

[0094] As shown in FIG. 2, a hub portion 162 extends down from thecentrifuge top wall 160. The hub portion 162 has an inner surface 164and an exterior surface 165, both of which are shown as beingsubstantially parabolic in shape. As discussed in further detail below,the hub portion 162 substantially reduces the volume of the centrifugechamber 152 and enhances the circular, centrifugal flow of fluid aboutthe hub portion within the centrifuge chamber 152.

[0095] Opposite the top wall 160, a contoured bottom insert 166 ispositioned within the centrifuge chamber 152. The contoured bottominsert 166 comprises a contoured top surface 170 and a contoured bottomsurface 172. The contoured top surface has an annular flat portion 174,an upward directed curved portion 176, and a conically shaped centralportion 180. As shown, each output 154 includes an output opening 182formed in the conically shaped portion 180.

[0096] As mentioned above, the centrifuge 136 also includes the seriesof tangentially oriented baffles 150 positioned within the entry chamber146. Each baffle 150 comprises leading edge 184, and an intermediatecorner 186 as well as a rounded trailing end 190. A leading flat surface192 is formed between the leading edge 184 and the corner 186. A flatsurface 194 is formed between the leading edge 184 and the trailing end190. Lastly, a surface 196 is formed between the corner 186 and thetrailing end 190.

[0097] The baffles 150 are aligned relative to one another so as tocreate a plurality of tangential fluid flow passageways 200 formedbetween the surfaces of adjacent baffles 150. Additionally, a tangentialpassageway 202 is formed between the surface 194 of a baffle 150adjacent to the vertically oriented wall 206 of the entry chamber 146.Moreover, a tangential passageway 204 is formed between the surface 192of a baffle adjacent to a vertical wall 210 of the entry chamber 146.

[0098] As shown in FIG. 1, each trailing flat surface 194 is oriented ata tangential angle relative to the annular wall 156 of the centrifugesection 36. Accordingly, the flow of fluid introduced into thecentrifuge chamber 152 through the passageways 200, 202, and 204 isintroduced in a direction substantially tangent to the annular wall 156to enhance the circular and centrifugal flow of fluid in the chamber152.

[0099] To secure the centrifuge housing 142 to an engine manifold (notshown), mounting locations 212, 214, and 216 are formed in thecentrifuge housing to permit fasteners, such as bolts 180 (FIG. 2) tosecure the centrifuge housing 142 to the engine via an interface plate143.

[0100]FIG. 7 illustrates an alternative embodiment of the presentinvention. This embodiment shows a vortex chamber assembly 220 whichgenerally comprises conventional electronic fuel injectors 222, a firstvortex chamber housing 224, and subsequent vortex chamber housings 226,228, 230, and 232. In this configuration, the chamber housings 226-232each receive a flow of fluid exclusively from the preceding chamberhousing. For example, the chamber housing 228 receives fluid exclusivelyfrom the output of chamber housing 226 and so on.

[0101] The fuel injectors 222 are mounted within bores 234 formed in aninjector plate 236. Each fuel injector includes an output port 240 whichsprays fuel into a preliminary mixing chamber 242. Ambient air isintroduced into the preliminary mixing chamber 242 via an ambient airconduit 244. The preliminary mixing chamber 242 and the ambient airconduit 244 are configured and function in a manner similar to theconfiguration and function of the preliminary mixing chamber 44 and theambient air conduit 50 illustrated in FIG. 1.

[0102] The chamber housings 224, 226, 228, 230, and 232 respectivelydefine vortex chambers 248, 250, 252, 254, and 256. The vortex chambers224-232 each have an array of apertures 260-268. Each array of apertures260-268 are arranged in a plurality of rows and a plurality of columnsin a manner similar to that illustrated in FIG. 3. Moreover, each arrayof apertures 260-268 are arranged in a staggered configuration so as toenhance the turbulence of a vertical flow through the respective vortexchamber 248-256.

[0103] Pressure differential supply inlets are formed by tapered jackets272, 274, 276, 278, and 280 positioned about the chamber housings 224,226, 228, 230, and 232, respectively. Each functions in a manner similarto the jacket 60 described in connection with FIG. 1. Each of thejackets 272-280 has a respective interior surface 284, 286, 288, 290,292. The jacket interior surfaces 284-292 each comprises a constantdiameter portion 296, 298, 300, 302, 304, respectively, and a variablediameter interior surface portion 308, 310, 312, 314, 316, respectively.Each chamber housing 224, 226, 228, 230, 232 has a respective exteriorsurface portion 318, 320, 322, 324, 326. The jackets Form variably sizedgaps 330, 332, 334, 336, 338 between the surfaces 330-338 and thesurfaces 308-316, respectively. As such, the variable spaced gaps allowa differential pressure of fluid at the various apertures 260-268according to the location of the apertures 260-268 and function in amanner similar to the gap 72 (FIGS. 1 and 2).

[0104] Additionally, each jacket 272-280 has a respective output port340-348 which is in fluid communication with the subsequent vortexchamber. FIGS. 8-10 illustrate the jacket 278 vortex chamber 254 ingreater detail. Each of the output ports 340-348 is in the form of aU-shaped slot represented by reference numeral 349 in FIGS. 9 and 10.The output ports 340-346 are in fluid communication with subsequentmixing chambers 350, 352, 354, and 356, respectively, so that theapertures 262-268 receive a fluid mixture exclusively from the outputports 340-346 to maintain a substantially constant air second fluidmixture as no additional air is introduced into the fluid stream as thefluid stream passes through the vortex chambers 250-256. Moreover, toenhance the mixing and vortical nature of the flow through the mixingchambers 242, 350, 352, 254, and 356, each chamber housing 224-232 has aconically tapered base portion 358.

[0105] Apertures 368 are formed in the jackets 274-280 for receivingfasteners (not shown), such as conventional set screws, to secure thejacket lower portions 370 to a preceding jacket's upper portion 372 orto a vaporizing housing 374.

[0106] FIGS. 11-13 illustrate an alternate embodiment of ajacket-chamber assembly for use in a plurality of vortex chamberconfigurations such as that illustrated in FIG. 7. Specifically, ajacket 376 is illustrated as having a constant diameter inside surface377, a variable diameter inside surface 378, an output port 379, andoutput apertures 381. The chamber housing 383 is shown as having aplurality of apertures 385 formed at an angle therein and leadingtangentially into a vortex chamber 387. A variably spaced gap 389 isformed between the interior surface 378 of housing 376 and the exteriorsurface 391 of the vortex chamber 383.

[0107]FIG. 14 shows another alternative embodiment of a vortex chamberaccording to the present invention. A chamber housing 380 having anexterior surface 382 and an inner chamber wall 384 defines a vortexchamber 386. To increase the turbulence of a vortical flow within thechamber 386, and to break down into smaller particles any non-vaporizedparticles in the vortical flow, steps 388 are formed on the innerchamber wall 384. As shown, each step 388 comprises a ramp surface 390and a transverse surface 392. A plurality of apertures ramp 394 areformed in the housing 380 and intersect the inner chamber wall 384 attransverse surfaces 392. As a fluid flows through the vortex chamber386, the steps 388 cause relatively small eddies to be created adjacentto the various transverse surfaces 392 which enhances the turbulence ofthe flow through the chamber 386.

[0108] As an alternative or additional manner of increasing theturbulence of a vortical flow within the chamber 386, and to break downinto smaller particles any non-vaporized particles in the vortical flowas well as enhance the vaporization of the non-vaporized particles, theinner chamber wall 384 may comprise a textured surface. The textured orirregular surface may be formed by heavy grit sand blasting or applyinga type of glass beading. A textured or irregular inner chamber wallsurface will tend to cause fluid to flow through the chamber 386 in amore turbulent manner. When non-vaporized particles collide with thetextured inner chamber wall surface, the non-vaporized particles willspread apart, break down into smaller particles, and vaporize morereadily as compared to a smooth inner wall surface.

[0109] FIGS. 15-17 illustrate yet another alternative embodiment of avortex assembly according to the present invention. As shown in FIG. 15,a centrifugal vortex system 400 generally comprises a fuel vaporizingsection 402 in fluid communication with a main air section 404. The mainair section 404 is in fluid communication with a centrifuge section 406.The fuel vaporizing section 402 includes a main air housing 410 whichhas inside surface 412. The inside surface 412 defines a main airchamber 414 into which ambient air is introduced. A base plate 416 isattached to the main air housing 410 along a main air housing edge 418.An injector plate 420 is secured within the base plate 416 by base plateextensions 422. Fuel injectors 424 (only one is shown in FIG. 15—theother fuel injector positioned directly behind the illustrated fuelinjector 424) are secured within the injector plate 20 for spraying fuelinto a first vortex chamber 426 formed in the chamber housing 428. Alsoformed in the chamber housing 428 are second vortex chamber 430, thirdvortex chamber 432, and fourth vortex chamber 434.

[0110] To permit air to enter the vortex chambers 426, 430, 432, and434, a plurality of apertures 436 (FIGS. 16 and 17) are formed at anangle in the chamber housing 428 so that the apertures enter into eachvortex chamber tangentially. Each aperture is oriented substantiallytangentially to inner surfaces 438-444 to permit air to be tangentiallyintroduced into each vortex chamber 428, 430, 432, and 434. Theapertures are preferably formed in an array of rows and columns, thecolumns being offset relative to each adjacent row.

[0111] To enhance the turbulence, pressure differentials, shear forces,and changes in velocity applied to the fluid as it passes through thechambers 428-434, the array of apertures 436 are advantageously orientedin opposite tangential directions in adjacent chambers. For example, theapertures in the chamber 428 are oriented to introduce fluid in a firstvortical flow direction within the chamber 428 and the apertures in thechamber 430 are oriented in a direction opposite to the orientation ofthe apertures in chamber 428 to introduce fluid in a second vorticalflow direction within chamber 430.

[0112] A pressure differential supply configuration formed by a taperedjacket 450, is provided around the outside of the series of vortexchambers. The jacket 450 is secured to an end 452 of the vortex chamberhousing 428. The jacket 450 generally comprises a tapered portion 454and an elongated tube portion 456. The jacket portion 454 is configuredand operates in a manner substantially similar to the manner ofoperation of jacket 60 (FIG. 1) and comprises an exterior surface 458and a variable diameter inner surface 460 to form a variable width gap462 between the inner surface 460 and the exterior surface 464.

[0113] The variably width gap 462 creates a varying degree of pressureresistance across the apertures 436 formed in the chamber housing 428.Where the gap is more narrow toward the downstream end 452 of thechamber housing, the fluid pressure is maximized. Fluid pressuredecreases from that point in an upstream direction toward chambers 432,430, and 428. In this configuration, the pressure resistance across theapertures 436 varies according to the location of a given aperture. Thejacket 450 also includes an output boss 470 which comprises an annularboss exterior surface 472 and an annular boss interior surface 474. Thepurpose and function of the jacket output boss is described below.

[0114] The tube portion 456 of the jacket 450 comprises an inner surface466 and an exterior surface 468. The interior surface 466 defines a tubehollow interior 470. A helically wound solenoid 476 is secured aroundthe tube portion 456 of the jacket 450 for selectively creating amagnetic field within the tube interior. An elongated conduit 478 formedintegrally with a conduit base 480 is slidingly positioned within thejacket tube portion 456 to permit the conduit base 480 to travel withinthe tube portion 456 between the positions illustrated in FIGS. 16 and17. A biasing member, such as a spring 482, is also disposed within thejacket tube portion 456 between the conduit base 480 and the jacketportion 454. The spring 482 selectively maintains the conduit base 480in the position illustrated in FIG. 17.

[0115] As shown in FIG. 17, when the solenoid 476 is not energized, theelongated conduit 478 is withdrawn from the vortex chambers 428-434. Theactivation of the solenoid 476 causes the conduit base 480 to move intothe position illustrated in FIG. 16, thus compressing the spring andadvancing the elongated conduit 478 through the chamber outputs 484,486, and 488 into direct communication with chamber output 490.Activating the solenoid 476 and causing it to move the elongated conduit478 into the position illustrated in FIGS. 15 and 16, causes thevortical flow through the housing 427 to be isolated in the vortexchamber 428 and permits the flow to selectively bypass the remainingchambers 430, 432, and 434.

[0116] Advantageously, the elongated conduit 478 is selectively, andbriefly, moved into position illustrated in FIGS. 15 and 16 forintervals on the order of 0.5 seconds during transient periods of engineacceleration and deceleration. By selectively isolating the chamber 428during these periods, a well-known problem of “acceleration stumble” issubstantially alleviated.

[0117] The problem of acceleration stumble generally occurs duringtransient periods of acceleration and deceleration. For example, withrespect to FIG. 15, during periods of acceleration, the throttle plate518 opens and thus causes the pressure in the main air chamber 414 todrop. This drop in pressure, in turn, causes a decrease in the amount ofair entering into the vortex chambers 426, 430, 432, and 434. With lessair entering the vortex chambers, a smaller portion of the fuel sprayedfrom the fuel injector 424 is carried through the vortex chambers andinto the engine, thus causing a relatively lean fuel mixture. Becausethe fuel during this period is not effectively passing through thevortex chambers, an amount of fuel accumulates in the vortex chambers426 and 430. Then, as the accumulated fuel passes through the remainingvortex chambers, a fuel-rich mixture is provided to the combustionengine (not shown). This period of fuel-lean fluid followed by theperiod of fuel-rich fluid and the associated engine difficultiesassociated with these drastically varying air-fuel ratios, is referredto as “acceleration stumble.”

[0118] Additionally, by employing the elongated conduit 478 as describedabove, the amount of hydrocarbons in the fluid is greatly decreased.Moreover, bypassing chambers 430-434 during acceleration anddeceleration will prevent chambers 430-434 from dominating the chamber428.

[0119] The main air intake section 404, as illustrated in FIG. 15includes a cylindrical air intake 500. An annular channel 502 is formedon the air intake port to facilitate the attachment of a conventionalambient air conduit (not shown). The air intake port 500 also introducesair into an ambient air conduit 508 formed in an intermediate housing510. As shown, the intermediate housing 510 is rigidly attached to themain air housing 410 and also includes concentric bores 512 and 514. Thedownstream end 518 of the jacket tube portion 456 is secured within thebore 512 to permit fluid discharged from the downstream end 518 to bepassed from the jacket tube portion 456 through the bore 514 into themain air intake section 404.

[0120] To regulate the volume of air admitted to the engine (not shown),a conventional throttle plate 518 is secured to a rotatable centralshaft 520, which is oriented transverse to the direction of air flowthrough the main air section 404.

[0121] The venturi 506 comprises a large diameter air intake opening522, a narrow throat portion 524, and a large diameter air/fuel mixtureoutput opening 526. The venturi 506 further comprises a venturi exteriorsurface 528 and a venturi interior surface 530. The diameter of theventuri interior surface 530 is minimized at the venturi narrow throat524 and maximized at the intake and output openings 522 and 526. Theventuri output opening 526 is in direct communication with a main airsection output channel 532 for discharging fluid from the main airintake section 404 into the centrifuge 406.

[0122] The centrifuge 406 comprises a generally cylindricalconfiguration. The centrifuge includes an annular wall 534 having anexterior surface 536 and an interior surface 538. The wall 534 isinterrupted by an intake opening 540 for receiving fluid from the outputchannel 532 of the venturi into a centrifuge chamber 542. The centrifugechamber 542 is further defined by a centrifuge top plate 544 and acentrifuge bottom plate 546.

[0123] A large diameter output aperture 548 is formed in the centrifugebottom plate 546 for discharging fluid from the centrifuge chamber 542.The output aperture 548 is defined by a rounded surface 550 having aminimum diameter 552 and a maximum diameter 554.

[0124] To enhance the vacuum pressure at the output aperture 548, theratio of the diameter of the venturi inside surface 530 at the throat524 to the minimum diameter 552 is greater than 1.58:1, preferablyapproximately 1.66:1.

[0125] The centrifuge housing 406 is securable to an engine (not shown),via apertures 558 formed in mounting flanges 556 extending from wall534.

[0126]FIG. 18 illustrates still another alternative embodiment of avortex chamber assembly according to the present invention. A chamberhousing 570 comprises an exterior surface 572 and interior surfaces 574,576, 578, 580, and 582. The interior surfaces 574-582 are eachsubstantially cylindrical and define, respectively, vortex chambers 584,586, 588, 590, and 592.

[0127] Apertures 594 are formed tangentially, in an array with offsetcolumns and rows, in the chamber housing 570 to allow the input of fluidtangentially into each vortex chamber 584-592. This tangential input offluid creates a turbulent vortical flow of fluid through the vortexchambers which breaks down the fluid into smaller particles andvaporizes remaining liquid particles in the vortical flow. The apertures594, as shown, are arranged in a plurality of rows and in a plurality ofcolumns, preferably staggered relative to one another, to furtherenhance the turbulent nature of the flow through the chambers 584-592.

[0128] A cylindrical output flange 596 comprises an exterior surface 598and an interior surface 600. The output flange is attached to anupstream end 602 of the chamber housing 570. The interior surface 600defines the output from vortex chamber 584 of the vortex chamber housing570. As illustrated, the vortex chambers 584-592 have sequentiallydecreasing diameters. That is, the diameter of the inside surface 582 issmaller than the diameter of inside surface 580, which is, in turn,smaller than the inside surface of surface 576, which is smaller thanthe inside surface 574. Given this configuration, as the fluid passesthrough the chambers 584-592 in a vortical flow having a low pressureend at the output 604 and a high pressure end adjacent to an upstreamend 606, the tendency for the chambers closest to the low pressure end(chambers 584 and 586) to receive more flow through the apertures 594than the chambers closest to the high pressure end 604 (chambers 590 and592) is significantly reduced.

[0129] Additionally, to enhance the vaporization of a fluid as it passesthrough the chambers 584-592, appropriately sized nozzles 608 (FIG. 18)are positioned at an upstream end of each of the chambers 584, 586, 588,and 590, respectively. The nozzles 608 cause the fluid passing throughthe vortex chambers to be subjected to additional pressuredifferentials, thus enhancing the vaporization and break down of fluidparticles. The nozzles 608 are preferably sized so as to be securedwithin the upstream end of the chambers 584-590 by a press-fitattachment.

[0130]FIG. 19 discloses a yet additional embodiment of the presentinvention. As shown, FIG. 19 discloses a vortex configuration 611comprising a chamber housing 612 having an exterior surface 614 andinterior surfaces 616, 618, 620, 622, and 624. The internal surfaces616-624 are substantially cylindrical and respectively define vortexchambers 626, 628, 630, 632, and 634. Apertures 636 are formedtangentially relative to interior surfaces 616-624 of the vortexchambers 626-634. The apertures 636 are formed in an array in thechamber housing 612 to allow the input of fluid tangentially into thevortex chambers 626-634. This tangential input of fluid creates avortical flow through the vortex chambers for breaking down into smallerparticles and further vaporizing or homogenizing liquid particles in thevortical flow.

[0131] A cylindrical output flange 640 is attached to an end 642 of thechamber housing 612. The output flange 640 comprises an interior surface644 and an exterior surface 646. An output port 648 is defined by theoutput flange interior surface 644. The output flange 640 is similar tothe output flange 596 (FIG. 17) except that the diameter of the insidesurface 644 is smaller than that of the inside diameter 600 (FIG. 17).Additionally, the output flange 640 includes an aperture 650, throughwhich a screw (not shown) can be selectively inserted as a way to adjustthe flow resistance through the output member 640. The more the screw isadvanced into the output port 648, the more air resistance is impartedto the vortical flow as the vortical flow passes through the output port648.

[0132] In general, the air resistance through a vortex configuration canbe varied by changing the diameter of the output aperture and/orchanging the diameter of the passageways between adjacent vortexchambers within the vortex configuration. The embodiment of FIG. 18shows a relatively large output and relatively small passageways betweenadjacent vortex chambers due to the nozzles 608. Conversely, theembodiment of FIG. 19 shows a smaller output and larger passagewaysbetween chambers. In some applications it has been found that theembodiment illustrated in FIG. 19 is preferable to the embodiment ofFIG. 18.

[0133]FIG. 20 illustrates a yet additional embodiment of the presentinvention. Specifically, FIG. 20 illustrates the chamber housing 570 ofFIG. 18 in combination with an adjustable cross-sectional area outputport 660 formed in an output housing 662. As shown, the output housing662 comprises an outside surface 664, an inside surface 666 and ispositioned adjacent to the output 604 of the chamber housing 570. Theinside surface 666 defines the output port 660 into which fluid flowsfrom the output 604.

[0134] The housing 662 also comprises an actuator mounting extension670. The mounting extension 670 comprises a cylindrical inside surface672 and a threaded inside surface 674. An actuator, such as a steppermotor 676, comprises a male threaded portion 680 which is securable tothe corresponding female threaded portion 674 of the actuator housing670.

[0135] The stepper motor 676 acts as a linear actuator to move a conicalblock 678 relative to a conical seat 681 formed in the conduit 668. Theconical seat 681 comprises a flat bottom surface 683 and a conicallyshaped side surface 685. The side surface 685 is sized to engage a sidesurface 687 of the block 678 when a conical block end surface 689contacts the conical seat bottom surface 683.

[0136] Accordingly, by selectively moving the conical block 678 relativeto the seat 681, the effective cross-sectional area of the passagewayformed by interior surface 666 may be selectively varied.Advantageously, the cross-sectional area of the conduit 668 may beincreased or decreased, depending on the desired output. Moreover, theair resistance through the output port 660 may be varied by moving theconical block 678 relative to the seat 681.

[0137]FIG. 21 shows another alternate embodiment of the presentinvention. This embodiment shows a centrifugal vortex system 700comprising a fuel vaporizing section 702, a main air section 704, and acentrifuge section 706. The fuel vaporizing section 702 is illustratedas having two fuel injectors 708 for inputting fuel into the centrifugalvortex system 700. The fuel injectors 708 are coupled to a fuel rail 710having a passageway 712 passing therethrough from an input end 714 to anoutput end 716. The input end 714 of the passageway 712 is coupled to aconventional fuel pump (not shown) and the output end 716 is coupled toa conventional fuel regulator (not shown) which is, in turn, coupled toa return line back to the fuel tank (not shown).

[0138] The fuel injectors 708 are mounted within the centrifugal vortexsystem 700 by injector plates 720. Fuel is sprayed from fuel injectoroutput ports 722 into two vortex configurations 611 each vortexconfiguration 611 being identical to the vortex configuration 611illustrated in FIG. 19. The two vortex configurations 611 are positionedadjacent to the fuel injector plates 720 and are in fluid communicationwith the output ports 722 of the fuel injectors 708 to allow aerosolfuel to be sprayed directly into the two vortex configurations 611 fromthe output ports 722.

[0139] The two vortex configurations 611 are mounted within an air box724. The air box 724 is shown as comprising a side wall 726, a side wall728, a base plate 730, and a top plate 732. An air chamber 734 is formedwithin the air box 724 as a conduit between an ambient air conduit 736and the apertures 636 (FIG. 19) formed in the vortex configurations 611.

[0140] The ambient air conduit 736 is illustrated as comprising a rubberhose 740. The ambient air conduit 736 interconnects an ambient air slot742 with the chamber 734 for providing ambient air to the vortexconfigurations 611. As shown, the hose 740 is coupled to the slot 742via a threaded connector 741.

[0141] The vortex configurations 611 are secured within the air box 724by a bracket 744 interposed between the output flange 640 (FIG. 19) ofeach vortex configuration 611 and the inside surface 748 of the topplate 732. The output port 648 (FIG. 19) of each vortex configuration611 discharges fluid into an intermediate mixing chamber 750 formed inthe main air section housing 752. The intermediate mixing chamber 750generally causes a spinning column of fluid exiting the output port 648(FIG. 19) to enfold and to mix turbulently prior to entering the venturi756 through a series of elongated apertures 770. The described activityof the fluid in the intermediate mixing chamber 750 further breaks downinto smaller particles and further vaporizes and homogenizes the liquidparticles in the vortical flow.

[0142] The main air section 704 further comprises an ambient air intakeport 760 to permit a flow of air F to enter the main air section 704through the port 760. A conventional throttle plate 762 is pivotallysecured within the venturi 756. The throttle plate 762 is secured to arotatable central shaft 764, which is oriented transverse to thedirection of air flow F through the venturi 756. Rotation of the shaft764 will adjust an inclination angle of the throttle plate 762 withinthe venturi 756, thereby changing the volume of air and thus theair/fuel mixture admitted to the engine.

[0143] As mentioned above, an air/fuel mixture passes from the vortexconfigurations 611 into the intermediate mixing chamber 750. Theair/fuel mixture then passes through the intermediate mixing chamberoutput 758 and into the venturi 756 through a series of elongatedapertures 770. Thus, within the venturi 756, ambient air passing acrossthe throttle plate 762 is mixed with an air/fuel mixture passing throughthe apertures 770.

[0144] The centrifuge section 706 is rigidly affixed to the main airsection housing 752 by fasteners such as screws 772 and 774. Thecentrifuge section 706 is shown as comprising a transition housing 776having an inside surface 778 and an outside surface 780. The insidesurface 778 defines a transition passageway 782 for passing fluid fromthe venturi 756 into a centrifuge chamber 784. As shown, the transitionpassageway 782 is oriented substantially tangentially to the centrifugalvortex system chamber 784 for inputting fluid into the centrifugechamber 784 in a substantially tangential manner. By orienting thetransition passageway 782 substantially tangentially to the centrifugechamber 784, the air resistance through the system is reduced and thecentrifugal flow of fluid through the centrifuge chamber 784 isenhanced.

[0145] An extension arm 788 is positioned adjacent to the passageway 782and extends into the centrifuge chamber 784 to prevent fluid fromre-entering the passageway 782 after being discharged into the chamber784. The extension arm 788 is shown as comprising a wall 790 having afront surface 792 and a rear surface 794. As shown, the extension arm788 is mounted on and extends from the transition housing 776. The frontsurface 792 and the rear surface 794 are intersected at one end bytransverse surface 796. Thus, as fluid flow from the venturi 756 passesthrough the intermediate chamber 782 into the centrifuge chamber 784,the return of fluid from the centrifuge chamber 784 back into theintermediate chamber 782 is substantially prevented, if not eliminated,by the presence of the extension arm 788. As illustrated, the frontsurface 792 of the extension arm 788 is curved to enhance thecentrifugal flow of fluid in the centrifuge chamber 784 while, at thesame time, substantially preventing fluid from re-entering thepassageway 782.

[0146] The centrifuge section 706 further comprises a verticallydirected cylindrical wall 798 having an inside surface 800 and anexterior surface 802. A centrifuge bottom surface 804 is positioned in asubstantially perpendicular orientation with the inside surface 800 ofthe centrifuge housing and has an output conduit 806 defined by acylindrical surface 808 for discharging fluid from the centrifugechamber 784 to an internal combustion engine intake manifold (notshown).

[0147] Mounting extensions 810 are illustrated as being mounted on theexterior surface 802 of the centrifuge housing 798 for securing thecentrifuge housing to an interface plate or other mounting apparatus inconnection with an internal combustion engine intake manifold. Eachmounting extension 810 further comprises an aperture 812 for passing afastener through the mounting extension.

[0148]FIG. 22 illustrates a yet additional alternate embodiment of acentrifugal vortex system according to the present invention. Thisembodiment shows a centrifugal vortex system 820. The centrifugal vortexsystem 820 is illustrated as comprising three sections: fuel vaporizingsection 822, a main air section 824, and a centrifuge section 826. Thefuel vaporizing section 822 is illustrated as having two fuel injectors828 mounted within an injector plate 830 for spraying fuel into apreliminary mixing chamber 832. The fuel injectors 828, fuel injectorplate 830, and preliminary mixing chamber 832 are configured and operatesubstantially the same as the fuel injectors 38, the injector plate 42,and the preliminary mixing chamber 43 illustrated in FIG. 1 anddescribed above.

[0149] The fuel vaporizing section 822 further comprises a vortexchamber housing 834 and a jacket 836 positioned within a housing 838.The vortex chamber housing 834, the jacket 836, and the housing 838 areconfigured and function in substantially the same manner as the vortexchamber housing 54, the jacket 60, and the housing 74 described aboveand illustrated in FIGS. 1 and 3. The housing 838 further comprises anambient air receiving chamber 840 for receiving ambient air from theambient air slot 842 via conduit 844 and aperture 846.

[0150] Ambient air and fuel are introduced into the vortex chamber 848from the preliminary mixing chamber 832 via apertures 850. The air/fuelmixture is output through an output port 852 into an intermediatechannel 854 defined by an inner wall surface 856 of an intermediatehousing 858.

[0151] A linear actuator, such as a stepper motor 860 identical to thestepper motor 676 illustrated in FIG. 20 and described above isthreadedly engaged within the intermediate housing 858 and isillustrated as being substantially aligned and coaxial with the outputport 852. The stepper motor 860 further comprises a conical plug 862.The stepper motor 860 acts as a linear actuator to move the conical plug862 via a shaft 864 relative to the output port 852 for selectivelyproviding flow resistance at the output port 852.

[0152] When the shaft 864 is in a fully extended position (not shown),the conical plug 862 contacts and substantially seals the output port852 to substantially prevent fluid passage through the output port 852.In the fully retracted position illustrated in FIG. 22, the conical plug862 provides little, if any, flow resistance. Thus, the closer theconical plug 862 is positioned to the output port 852, the more fluidresistance will be imparted by the conical plug 862. As such, the flowresistance through the output port 852 can be varied by causing thestepper motor 860 to selectively position the conical plug 862 relativeto the output port 852.

[0153] After fluid passes from the output port 852 past the conical plug862 and into the intermediate channel 854, the fluid next enters themain air section 824. As shown, the main air section 824 comprises amain air housing 870, a venturi 872, and a conventional throttle plate874. The main air section 824 is configured and operates insubstantially the same manner as the main air section 34 described aboveand illustrated in FIG. 1. The throttle plate 874 is pivotally securedto a rotatable central shaft 878, which is oriented transverse to thedirection of air flow F through the chamber 876. Rotation of the shaft878 will adjust an inclination angle of the throttle plate 874 withinchamber 876, thereby changing the volume of air and thus the air/fuelmixture admitted to the engine.

[0154] Ambient air passes past the throttle plate 874 into the venturi872 through a venturi input 880. An air/fuel mixture enters the venturi872 through a series of elongated apertures 882 from the channel 854.The venturi input 882 is secured within an interior surface 884 of thehousing 870. The venturi output 886 is attached to the centrifugehousing 890.

[0155] The centrifuge housing 890 comprises an entry chamber 892 and acentrifuge chamber 894. The entry chamber 892 is defined by a curvedinside surface 896 and flat inside surface 898. A series of baffles 900are oriented tangentially relative to the centrifuge chamber interiorsurface 902. Each baffle 900 comprises a vertically directed wall 904having a curved surface 906 and a flat surface 908. The curved surface906 and the flat surface 908 of each baffle intersect at a leading edge910 and at a trailing edge 912. The baffles 900 form a plurality oftangential passageways 914 for inputting fluid tangentially from theentry chamber 892 into the centrifuge chamber 894.

[0156] A tangential passageway 916 is also formed between the flat edge898 of the entry chamber 892 and the flat edge 908 of the baffle 900adjacent to the flat edge 898 for admitting fluid tangentially into thecentrifuge chamber 894. Likewise, a tangential passageway 918 is formedbetween the curved surface 906 and a flat surface 920 formed on thechamber housing 890 for admitting fluid tangentially into the centrifugechamber 894.

[0157] An extension arm or diverter 924 is illustrated as beingintegrally formed with the chamber housing 890 and terminates at edge926. The extension arm 924 eliminates or substantially prevents fluidfrom the chamber 894 from exiting the chamber through the entry chamber892. Indeed, the extension arm 924 directs fluid passing adjacent to theentry chamber 892 away from the passageway 916. While configuredslightly differently, the extension arm 924 and the extension 788illustrated in FIG. 21 serve essentially the same purpose, that is toprevent fluid from escaping the centrifuge chamber and passing back intothe venturi.

[0158] The centrifuge section 826 further comprises output passagewaysconfigured identical to output passageways illustrated in FIG. 1 anddescribed above. The centrifuge chamber bottom surface 932 alsocomprises a contoured bottom insert identical to the contoured bottominsert 166 illustrated in FIGS. 1 and 2.

[0159] Mounting apertures 934, 936, and 938 are also formed in thechamber housing 89 to permit the chamber housing to be rigidly securedvia an interface plate (not shown) to an intake manifold of an internalcombustion engine.

[0160]FIG. 23 shows yet another alternate embodiment of a vortex chamberhousing according to the present invention. This embodiment shows avortex chamber housing 940 generally comprising a bottom wall 942 and aperpendicularly extending cylindrical wall 944. The cylindrical wall 944comprises an inside surface 946, a top edge 947, and an outside surface948. A vortex chamber 952 is defined by the inside surface 946 and thebottom wall 942. The vortex chamber housing 940 may be used in a mannersimilar to that of the vortex chamber housing 54 illustrated in FIG. 1and described above.

[0161] A series of elongated tangential slots 950 are formed through thewall 944 from the outside surface 948 to the inside surface 946 fordelivering a fluid tangentially into the vortex chamber 952 relative tothe vortical flow of fluid inside the chamber. Each slot 950 is shown asextending without interruption from the top edge 947 of the wall 944 tothe chamber housing bottom wall 942. The slots 950 are orientedtangentially to the inside cylindrical surface 946 of the annular wall944 to permit fluid to be introduced tangentially to the vortical flowinto the vortex chamber 952 of the vortex chamber housing 940.

[0162] Introducing fluid tangentially into the chamber 952 through theelongated slots 950 creates a continuous sheet of moving fluid passingrapidly across the vortex chamber interior surface 946 adjacent therespective slots 950. This substantially prevents any non-vaporizedparticles within the flow of fluid from congregating on the interiorsurface 946. As droplets of non-vaporized fluid particles approach orcontact the inside surface 946, such non-vaporized particles are blownaway from the inside surface by new fluid-flow particles entering thevortex chamber 952 through the slots 950. Any number of slots 950 may beemployed to achieve the desired results. Additionally, different widthsof the slots 950 may be used. The slots 950 may be formed in the annularwall 944 with a laser, a circular saw, or by any other suitable method.As one example, slots 950 may have a width of approximately 0.01 inches.

[0163]FIGS. 24 and 25 illustrate another alternate embodiment of aventuri according to the present invention. This embodiment shows aventuri 954 comprising a housing 956 and a series of tangentialapertures 958 formed in the housing 956. The tangential apertures extendfrom a housing exterior surface 955 to a housing interior surface 957.The apertures 958 are formed tangentially in the housing 956 to permitfluid, such as an air/fuel mixture, to be inserted into the venturiinterior 960 tangentially through the apertures 958 to enhance theturbulence of the flow through the venturi 954.

[0164] As shown, the tangential apertures 958 are formed within a narrowthroat portion 959 of the venturi 954. In the narrow throat portion 959,the speed of the fluid F passing through the venturi 954 is at amaximum. By introducing a second fluid tangentially into the venturiinterior 960 through the tangential apertures 958 in the narrow throatportion 959, the turbulence and mixing of the two fluids is enhanced.Delivery of the second fluid tangentially into the venturi interior 960through the tangential apertures 958 causes the flow through the venturiinterior 960 to spin, thus increasing the turbulence of the flow. Theenhanced turbulence of the flow through the venturi 954 further enhancesthe vaporization and homogenization of the fluid passing through theventuri 954. Accordingly, as the fluid flow F passes through the venturifrom the venturi entrance 962 to the venturi 964, the flow isintersected by a tangential flow of a second fluid, such as an air/fuelmixture, entering the venturi interior 960 through the tangentialapertures 958 to create a turbulent, and substantially helical, flowthrough the venturi 954.

[0165] FIGS. 26-30 illustrate a yet additional alternate embodiment of acentrifugal vortex system according to the present invention. FIG. 27shows a centrifugal vortex system 970 which generally comprises a vortexchamber assembly 972, a primary throat 973, a secondary throat 977, aprimary stepper motor 979, and a secondary stepper motor 981. As shownin FIGS. 27 and 28, the vortex chamber assembly 972 is configured in amanner similar to the vortex chamber assembly 822 illustrated in FIG.22. Specifically, the vortex chamber assembly 972 is illustrated ashaving two fuel injectors 974 mounted within an injector plate 975 forspraying fuel into a preliminary mixing chamber 976. The fuel injectors974, the fuel injector plate 975, and the preliminary mixing chamber 976are configured and operate in substantially the same manner as the fuelinjectors 828, the fuel injector plate 830, and the preliminary mixingchamber 832 illustrated in FIG. 22 and described above.

[0166] The vortex chamber assembly 972 further comprises a vortexchamber housing 978 and a jacket 980 positioned about the vortex chamberhousing 978 within a fuel vaporizing housing 982. The vortex chamberhousing 978, the jacket 980, and the fuel housing 982 are configured andfunction in substantially the same manner as the vortex chamber housing834, the jacket 836, and the fuel vaporizing housing 838 described aboveand illustrated in FIG. 22. The housing 982 further comprises an ambientair receiving port 984 (FIG. 28) for receiving ambient air into thepreliminary mixing chamber 976 through an annular conduit 986. A setscrew 988 is threadedly engaged with the fuel injector plate 975 andsecures the vortex chamber housing 978 within the vortex chamberassembly 972.

[0167] As shown in FIGS. 27 and 28, ambient air and fuel are introducedinto the vortex chamber 990 via apertures 992. Ambient air is introducedinto the preliminary mixing chamber 976 through the conduit 986. Fuel isdelivered into the preliminary mixing chamber 976 by injectors 974. Theair and fuel are allowed to mix in the preliminary mixing chamber priorto entering the vortex chamber 990. The air/fuel mixture is then drawninto the vortex chamber 990 through an array of tangential apertures 992to create a vortical flow of fluid in the vortex chamber 990. Thevortical flow serves to break down moisture particles. After spinningvertically in the chamber 990, the air/fuel mixture is output through anoutput port 994 into the primary throat 973 through an aperture 996formed in an intermediate housing 998. The intermediate housing 998 issecured to the housing 982 along a contact surface 999 such that theoutput port 994 and the aperture 996 are substantially aligned.

[0168] With continued reference to FIG. 27, a primary linear actuator,such as a stepper motor 979, is threadedly engaged with the intermediatehousing 998 and is shown as being substantially aligned and coaxial withthe aperture 996 and the output port 994. The stepper motor is identicalto the stepper motor 676 illustrated in FIG. 20 and described above. Aconical plug 1000 is coupled to the stepper motor 978 via aspring-biased shaft 1002. The stepper motor 979 acts as a linearactuator to move the conical plug 1000, via a shaft 1002, relative tothe aperture 996 and the output port 994 to selectively restrict theflow through the output port 994.

[0169] When the shaft 1002 is in a fully extended position (not shown),the conical plug 1000 engages, and substantially seals, the aperture 996to substantially prevent fluid passage through the output port 994 intothe primary throat 973. In a fully retracted position (not shown), theconical plug 1000 provides little, if any, flow resistance. Thus, thecloser the conical plug 1000 is positioned to the output port 994 andthe aperture 996, the more flow resistance is imparted by the conicalplug 1000. As such, the flow resistance through the output port 994 andthe aperture 996 can be controlled by causing the stepper motor 979 toselectively position the conical plug 1000 relative to the aperture 996and the output port 994.

[0170] After fluid passes from the output port 994, through the aperture996, and past the conical plug 1000, the fluid enters the primary throat973. As shown, the throat 973 comprises a passageway formed in theintermediate housing 998 and in the output housing 1004. Within theintermediate housing 998, the primary throat 973 is defined by aninterior surface 1006. Similarly, within the output housing 1004, theprimary throat 973 is defined by an interior surface 1008. The outputhousing 1004 further comprises a plurality of mounting apertures 1005for securing the centrifugal vortex system 970 to a conventional engine(not shown).

[0171] An aperture 1010 is formed in the intermediate housing 999 fromthe interior surface 1006 of the primary throat 973 to an interiorsurface 1007 of the secondary throat 977. As shown, the aperture 1010defines a passageway 1111 which interconnects the primary throat 973with the secondary throat 977. Thus, when the passageway 1111 is notblocked, fluid may flow from the primary throat 973 into the secondarythroat 977 through the passageway 1111.

[0172] A secondary linear actuator, such as stepper motor 981, is alsothreadedly engaged with the intermediate housing 998 and is illustratedas being substantially aligned and coaxial with the aperture 1010 and iscoupled to a conical plug 1012 via a shaft 1014. The stepper motor 981acts as a linear actuator to move the conical plug 1012, via the shaft1014, relative to the aperture 1010 for selectively providing flowresistance or substantially sealing the aperture 1010.

[0173] When the shaft 1014 is in a fully extended position (not shown),the conical plug 1012 contacts and substantially seals the aperture 1010to substantially prevent fluid passage from the primary throat 973 intothe secondary throat 977 through the passageway 1111. In a fullyretracted position (not shown), the conical plug 1012 imparts little, ifany, flow resistance to a flow of fluid passing from the primary throat973 into the secondary throat 977 through the passageway 1111. Thus, thecloser the conical plug 1012 is positioned to the aperture 1010, themore flow resistance is imparted by the conical plug 1012. As such, theflow resistance, and thus the flow, through the passageway 1111 can becontrolled by actuation of the stepper motor 981 to selectively positionthe conical plug 1012 relative to the aperture 1010.

[0174] As shown in FIGS. 27 and 29, a primary venturi 1020 is positionedwithin an interior surface 1008 of the primary throat 973. Similarly, asecondary venturi 1022 is positioned within an interior surface 1024 ofthe secondary throat 977. The venturis 1020 and 1022 are configured andoperate in substantially the same manner as the venturi 872 illustratedin FIG. 22. It should be noted that, however, the venturi 954illustrated in FIGS. 24 and 25 and described above may also beeffectively employed in this embodiment.

[0175]FIG. 29 illustrates that ambient air enters the system 970 throughambient air ducts 1021 and 1023. The air ducts 1021 and 1023respectively define duct interior passageways 1025 and 1027. To controlthe amount of ambient air entering the venturis 1020 and 1022 throughthe respective venturi openings 1026 and 1028, throttle plates 1030 and1032 are provided. The throttle plates 1030 and 1032 are pivotallysecured to rotatable shafts 1034 and 1036, respectively. The rotatableshafts 1034 and 1036 are oriented transverse to the direction of airflowthrough the venturis 1020 and 1022. The rotation of the shafts 1034 and1036 adjusts an inclination angle of the throttle plates 1030 and 1032,respectively, thereby changing the volume of air and thus the air/fuelmixture admitted to the engine. As shown in FIG. 28, the throttle plates1030 and 1032 are secured to the shafts 1034 and 1036 respectively byfasteners, such as screws 1040 (FIG. 28).

[0176] As illustrated in FIGS. 27 and 29, the secondary throat 977 islarger, and thus capable of accommodating more flow, than the primarythroat 973. Similarly, the secondary venturi 1022 is larger, and thuscapable of accommodating more flow than the primary venturi 1020. Asdiscussed in more detail below, the primary throat 973 and the primaryventuri 1020 are used exclusively at lower engine RPM's to enable a highresolution engine response. At higher engine RPM's, both the primary andsecondary throats 973 and 977 are utilized to enable the system toattain a high volumetric efficiency.

[0177] With reference to FIGS. 26, 28, and 30, the position of thethrottle plates 1030 and 1032 is controlled by a linkage assembly 1042.The linkage assembly 1042 is shown as generally comprising a primarylever arm 1044, a connecting link 1046, and a secondary lever arm 1048.The secondary arm 1048 is biased toward the closed position shown inFIGS. 26 and 30. The primary arm 1044 is rigidly secured to the primaryshaft 1034 such that as the primary arm 1044 pivots relative to theoutput housing 1004, the primary shaft 1034 also pivots, thus causingthe primary throttle plate 1030 to pivot. Likewise, the secondary arm1048 is rigidly secured to the secondary shaft 1036 so that as thesecondary arm 1048 rotates relative to the output housing 1004, thesecondary shaft 1036, and thus the secondary throttle plate 1032, arecaused to pivot. The link 1046 is shown as being pivotally secured tothe primary arm 1044 through an aperture 1050. The opposite end of thelink is slidably positioned within an elongated slot 1052 formed in thesecondary arm 1048.

[0178] With reference to FIGS. 26 and 30, the linkage assembly 1042 isillustrated as being in a closed position with both the primary andsecondary throttle plates 1030 and 1032 being substantially closed. Asthe primary arm 1044 rotates about the primary shaft 1034 in a clockwisedirection, the primary throttle plate 1030 (FIG. 28) opens and admitsair into the primary venturi 1020 (FIG. 29). Additionally, as theprimary arm 1044 rotates clockwise, the link 1046 slides along the slot1052 formed in the secondary arm 1048. As the primary arm 1044 continuesto rotate clockwise, further opening the primary throttle plate 1030,the link 1046 advances through the slot 1052 until it contacts the slotend 1054. Once the link 1046 has contacted the slot end 1054, anyadditional clockwise rotation of the primary arm 1044 causes thesecondary arm 1048 to rotate, thus causing the secondary throttle plate1032 to pivot and open the secondary throat. The link 1046 contacts theslot end 1054 when the primary throttle plate 1030 is opened apredetermined amount. In one embodiment, this predetermined amount isapproximately 40% open.

[0179] By continuing to rotate the primary arm 1044 clockwise after thelink 1046 is in contact with the slot end 1054, the link 1046 causes thesecondary arm 1048 to rotate clockwise, thus opening the secondarythrottle plate 1032. That is, once primary throttle plate is opened 40%toward being fully opened, the link 1046 engages the slit end 1054 andthe secondary throttle plate 1032 starts to open. In the filly openposition illustrated in phantom in FIG. 30, the primary and secondaryarms 1044 and 1048 are oriented such that both throttle plates 1030 and1032 are fully open. As discussed in more detail below, rotating theprimary arm 1044 counterclockwise causes the primary and secondarythrottle plates 1030 and 1032 to close.

[0180] With reference to FIG. 27, it is advantageous for the secondarylinear actuator 981 to remove the conical plug 1012 from within theaperture 1010 as the secondary throttle plate 1032 begins to open. Inthis manner, the primary throat 973 is the exclusive flow path for theair/fuel mixture at low engine RPM's when the primary throttle plate1030 is opened less than a predetermined amount, such as 40%. As theprimary throttle plate continues to open past the predetermined amount,the plug 1012 is removed from the aperture 1010 and the secondarythrottle plate 1032 is opened to permit the air/fuel mixture to passthrough both the primary and secondary throats 973 and 977 to enhancethe volumetric efficiency of the system at higher engine RPM's. Thepositions of the throttle plates 1030 and 1032 can be continuouslymonitored by throttle plate sensors coupled to the shafts 1034 and 1036through sensor connectors 1037 and 1039 (FIG. 26). Accordingly, in thismanner, a relatively high resolution response can be attained at lowengine RPM's by using the smaller primary throat 973 exclusively. Then,at higher engine RPM's, when volumetric efficiency is desired, thesecondary throat 977 may be used in addition to the primary throat 973.

[0181]FIG. 31 shows another alternative embodiment of the presentinvention. The embodiment of FIG. 31 generally demonstrates that thestructures and methods illustrated in FIGS. 26-30, described above, canalso be used in connection with a four-barrel carburetor system. Oneside of the four-barrel system is essentially a mirror image of theother. Specifically, FIG. 31 illustrates two vortex chamber assemblies1060 and 1062. Each vortex chamber assembly 1060 and 1062 is configuredidentically to and operates in the same manner as the vortex chamberassembly 972 illustrated in FIGS. 27 and 28 and described above.Likewise, the embodiment of FIG. 31 illustrates two primary linearactuators 1064 and 1066. The primary linear actuators 1064 and 1066 areconfigured and operate in the same manner as the primary linear actuator979 illustrated in FIG. 27 and described above. Further, FIG. 31illustrates two secondary linear actuators 1068 and 1070 which areconfigured and operate the same as the secondary linear actuator 981illustrated in FIG. 27 and described above.

[0182] The linear actuators 1064 and 1068 are mounted within a firstintermediate housing 1072. The intermediate housing 1072 is configuredand operates in a manner identical to that of the intermediate housing998 illustrated in FIG. 27 and described above. Likewise, the linearactuators 1066 and 1070 are also mounted within an intermediate housing1074 which is configured and operates in a manner identical to theintermediate housing 998 illustrated in FIG. 27 and described above.

[0183] An output housing 1078 is positioned between the intermediatehousings 1072 and 1074. The output housing 1078 is similar to the outputhousing 1004 illustrated in FIGS. 26-29 and described above. The primarydifference between the output housing 1078 and the output housing 1004is that the output housing 1078 is configured with two adjacent primarythroats and two adjacent secondary throats for accommodating flowthrough two primary throttle plates 1080 and 1082 and two secondarythrottle plates 1084 and 1086 respectively.

[0184] The primary throttle plates 1080 and 1082 are configured andoperate the same as the primary throttle plate 1030 illustrated in FIG.29 and described above. Likewise, the secondary throttle plates 1084 and1086 are configured and operate in the same manner as the secondarythrottle plate 1032 illustrated in FIG. 29 and described above. Theprimary throttle plates 1080 and 1082 are both rigidly attached to asingle primary shaft 1090 by fasteners 1092. Likewise, the secondarythrottle plate 1084 and 1086 are secured to a secondary shaft 1094 byfasteners 1096.

[0185] The positions of the primary throttle plates 1080 and 1082 aswell as the positions of the secondary throttle plates 1084 and 1086 arecontrolled by a linkage system 1100. The linkage system 1100 comprises aprimary arm 1102, a secondary arm 1104, and a link 1106. The primary arm1102, the secondary arm 1104, and the link 1106 are configured andoperate in substantially the same manner as the primary arm 1044, thesecondary arm 1048, and the link 1046 of the linkage system 1042illustrated in FIGS. 26 and 30 and described above. Further, to monitorthe positions of the throttle plates, throttle plate sensors 1108 and1110 are coupled with the shafts 1090 and 1094 respectively. The outputhousing 1078 may be readily secured to a conventional engine (not shown)by conventional mounting apertures 1112.

[0186]FIGS. 32 and 33 illustrate a yet additional alternative embodimentof the present invention, specifically in relation to uses in the fieldof inhaler-type medications. This embodiment shows a fluid vaporizationsystem 1120 generally comprising a compressible container 1122, a supplyof pressurized gas 1124, a venturi 1126, a plurality of vortex chamberhousings 1128, 1244, 1248, 1250, 1252, 1254, 1256, 1258, and a systemoutput 1128. Generally, by introducing pressurized gas into the system1120, a fluid flow 1130 is forced out of the compressible container 1122and is caused to flow through conduits 1132 and 1134 (formed in the base1136) and into the venturi 1126 (also formed in the base 1136). In theventuri 1126, the fluid 1130 is mixed with pressurized gas and isdischarged from the venturi 1136 as an aerosol through the venturioutlet opening 1138. The fluid then passes through a series of vortexchamber housings for breaking down into smaller particles and furthervaporizing any non-vaporized or partially vaporized particles in theflow. Lastly, the fluid is output from the system through the systemoutput 1128.

[0187] Specifically, as shown in FIG. 33, the compressible container1122 is illustrated as comprising a bag having a flexible side wall 1140and a flexible base 1142. The flexible wall 1140 and flexible case 1142define a hollow interior 1144 within the compressible container 1122. Asthe compressible container 1122 is compressed, the volume of the hollowinterior of 1144 is reduced, thus increasing the pressure within thehollow interior 1144.

[0188] A compressible fluid container output port 1160 is defined by aninterior surface 1161 of a connector 1148. Advantageously, the connector1148 is formed of a pliable material, such as rubber. The connector 1148is coupled with the base 1136 via a barbed connector 1150. The barbedconnector 1150 is shown as comprising a threaded portion 1152, ashoulder 1154, and a barbed extension 1156. A raised barb 1158 is formedon the extension 1156 to allow a resistance or interference fit betweenthe barbed connector 1150 and the connector 1148 of the container. Thebarbed connector 1150 further comprises a passageway 1159 extending fromthe output port 1160 to the conduit 1132 to permit the fluid 1130 withinthe hollow interior 1144 of the compressible container 1122 to pass fromthe container 1122 into the conduit 1132. Accordingly, in the assembledconfiguration shown in FIGS. 32 and 33, the threaded portion 1152 of theconnector 1150 is threadedly engaged with the base 1136. Thecompressible container 1122 is, in turn, removably secured by aresistance or an interference fit with the barbed connector 1150 bypressing the pliable connector 1148 over the extension 1156 so that atight resistance or interference fit is created between the barbedextension 1156 and the interior surface 1161 of the connector 1148.

[0189] The compressible container 1122 is shown as being positionedwithin a pressure chamber 1164 defined by an interior surface 1166 of apressure housing 1168. The pressure housing 1168 is secured to the base1136 by threads 1170 formed on one end of the pressure housing 1168 forthreadedly engaging the pressure housing 1168 with the base 1136. Tocreate a substantially airtight seal between the base 1136 and thehousing 1168, a gasket, such as an O-ring 1172, is positioned, andpreferably compressed, between a flange 1174 of the housing 1168 and acontact surface 1176 of the base 1136.

[0190] The pressure chamber 1164 is pressurized by receiving pressurizedgas from the source of pressurized gas 1124 through a pressurized gasconduit 1178. The source of pressurized gas may advantageously becoupled with any of a variety of suitable devices, such as a pump ortank of pressurized gas. Further, the pressurized gas may comprise air,oxygen, nitrous oxide or any other suitable gas.

[0191] The pressurized gas conduit 1178 is shown as being formed in thebase 1136 and as extending from venturi inlet opening 1180 to thepressure chamber 1164. By passing pressurized gas through the conduit1178 into the pressure chamber 1164, the pressure within the pressurechamber 1164 increases. This increase of chamber pressure causes thecompressible container 1122 to compress, thus squeezing the fluid 1130out of the container 1122 through the output port 1160 and the connectorpassageway 1159.

[0192] As shown in FIG. 33, the contents of the compressible container1122 may comprise liquefied fluid 1130 and, in some instances, an amountof gas-phase fluid, such as air 1182. The system 1120 may be used tovaporize a wide range of fluids. In one embodiment, the liquefied fluid1130 to be vaporized comprises a medicinal preparation to beadministered to a patient by inhalation. Preferably, as the fluid exitsthe system through the system output 1128, only a small percentage ofthe non-vaporized fluid particles are greater than five microns in size.By vaporizing a fluid medicinal preparation by passing it through thesystem 1120, the medicinal preparation may be effectively administeredto a patient by inhalation.

[0193] A flow regulator or ball valve assembly 1184 is coupled to thefluid conduit 1132 extending from the output port 1160. The flowregulator 1184 is shown as generally comprising a regulator housing1186, a ball 1188 which seats into an appropriately sized cavity, anadjustment screw 1190, and a bias member 1192. The flow regulatorhousing 1186 is removably secured to the base 1136 by a threadedengagement. As shown, the ball 1188 seats within a spherical opening1194 formed in the base 1136. The ball 1188 is biased against thespherical opening 1194 by means of a bias member 1192. As illustrated inFIG. 33, the bias member 1192 may comprise a conventional coil spring.In this configuration, as the pressure within the hollow interior 1144of the compressible container 1122 increases, the pressure within theconduit 1132 increases correspondingly, thus overcoming the bias andpushing the ball 1188 away from the spherical opening 1194 to permitfluid to pass by the ball 1188 from the conduit 1132 into the conduit1134.

[0194] The amount of pressure necessary to unseat the ball 1188 from thespherical opening 1194 may be adjusted by adjusting the compression ofthe bias member 1192. The compression, and thus the force exerted by thebias member 1192, is readily adjusted by advancing or withdrawing theadjustment screw 1190 relative to the housing 1186. The farther thescrew 1190 is advanced into the housing 1186, the more compressed thebias member 1192 will be and, consequently, the more pressure will berequired to unseat the ball 1188 to permit fluid to pass by theregulator assembly 1184. Conversely, as the screw 1190 is withdrawn fromthe housing 1186, the compression of the bias member 1192 is decreased,and thus a lesser pressure within the conduit 1132 will be required tounseat the sphere 1188.

[0195] The ball valve assembly 1184 is only one of many differentregulators that can be effectively used to control the flow of fluidbetween the conduits 1132 and 1134. It is to be understood that anysuitable valve or other flow-regulating devices may be effectivelyemployed.

[0196] In addition to supplying pressurized gas to the pressurized gasconduit 1178, the source of pressurized gas 1124 also feeds pressurizedgas into the venturi 1126 through a venturi inlet opening 1180. Theventuri 1126 generally comprises the venturi inlet opening 1180, aventuri outlet opening 1196, and a narrow throat portion 1198. Thenarrow throat portion 1198 is shown as being positioned between theventuri inlet opening 1180 and the venturi outlet opening 1196.

[0197] As a flow F of pressurized gas from the pressurized gas source1124 passes through the venturi 1126, the narrow throat portion 1198causes the velocity of the pressurized gas to substantially increase.The high speed of the gas through the venturi throat portion 1198creates a low pressure region at the venturi throat portion 1198. Asshown, the narrow throat portion 1198 is in fluid communication with theconduit 1134. The low pressure region at the narrow throat portion 1198helps to draw fluid from the conduit 1134 into the high-speed,low-pressure gas flow through the venturi throat portion 1198. As thefluid 1130 passes through the conduit 1134 into the narrow throatportion 1198, the fluid 1130 is mixed with the pressurized gas from thepressurized gas source 1124. Because of the high velocity of the gaspassing through the narrow throat portion 1198 and the pressuredifferentials created by the venturi 1126, the fluid 1130 advantageouslyexits the venturi 1126 through the venturi outlet opening 1196 as anaerosol.

[0198] After exiting the venturi 1126, the fluid is discharged into amixing chamber 1200 through a plurality of apertures 1202 formed in ahollow boss 1204. As shown in FIG. 33, the boss 1204 is formed as onepiece with the base 1136 and comprises a hollow interior 1206 in fluidcommunication with the venturi outlet opening 1196. Thus, upon exitingthe venturi 1126 through the venturi outlet opening 1196, the fluidpasses into the mixing chamber 1200 through the apertures 1202 formed inthe boss 1204.

[0199] The mixing chamber 1200 is defined by a base exterior surface1210, an inside surface 1212 of a tube 1214, and the exterior surface1216 of the venturi chamber housing 1128. The vortex chamber housing1128 is configured and functions in the same manner as the vortexchamber housing 940 described above and illustrated in FIG. 23.

[0200] As shown in FIG. 33, the vortex chamber housing 1128 furthercomprises an exterior bottom surface 1220 which is positioned adjacentto and abuts the boss 1204, causing the fluid passing through the bosshollow interior 1206 to exit the hollow interior through the apertures1202. After the flow F of fluid enters the mixing chamber 1200, thefluid next passes into the vortex chamber 1124 through tangentialapertures 1220 formed in the vortex chamber housing 1128. The tangentialslots 1222 are identical to the elongated tangential slots 950 describedabove and illustrated in FIG. 23. The tangential slots 1222 permit thefluid to be directed tangentially into the vortex chamber 1224. Due tothe tangential orientation of the slots 1222, the fluid is directedtangentially into the vortex chamber 1224 to create a vortical flow offluid within the vortex chamber 1224.

[0201] An output fixture 1230 is attached to the vortex chamber housing1128 for directing the fluid from the vortex chamber 1224 into a mixingchamber 1232. The output fixture 1230 is illustrated as being attachedto the vortex chamber housing 1128 by a press-fit attachment, but couldalso be secured to the vortex housing by a number of conventionalmethods.

[0202] The output fixture 1230 is shown in FIG. 33 as comprising a body1234 having an annular groove 1236 formed about the periphery of thebody 1234. A gasket, such as O-ring 1238, may be positioned within thegroove 1236 to prevent the fluid from passing directly from the mixingchamber 1200 to the mixing chamber 1232 without passing through thevortex chamber 1224. The output fixture 1230 further comprises a hollowinterior 1240 and apertures 1242 for directing the fluid from the vortexchamber 1224 through the output fixture 1230 into the mixing chamber1232. Upon exiting the output fixture 1230 through the apertures 1242,the fluid passes through the mixing chamber 1132 and through the vortexchamber housing 1244 in the same manner as the fluid passes through thevortex chamber housing 1128. Likewise, the fluid exits the vortexchamber housing 1244 through an output fixture 1246 which is configuredidentical to the output fixture 1230 discussed above and illustrated inFIG. 33. In this same manner, as shown in FIG. 32, the fluid passesthrough the vortex chambers 1248, 1250, 1252, 1254, 1256, and 1258 aswell as through output fixtures 1260, 1262, 1264, 1266, 1268, and 1270.As shown, the vortex chamber housings 1244, 1248, 1250, 1252, 1254,1256, and 1258 are each configured and function in a manner identical tothat of the vortex chamber housing 1128. Likewise, the output fixtures1246, 1260, 1262, 1264, 1266, 1268, and 1270 are configured and functionin a manner identical to that of the output fixture 1230 described aboveand illustrated in FIG. 33. Accordingly, no further description of thesefeatures is necessary.

[0203] Upon exiting the output fixture 1270 (FIG. 32), the fluid entersa discharge chamber 1272 defined by the output fixture 1270 and aninside surface 1274 of an output housing 1276. As shown, the outputhousing 1276 is rigidly secured to the tube 1214. The inside surface ofthe output housing 1276 while the discharge housing 1276 is illustratedas being attached to the tube 1214 by a press-fit attachment, thedischarge housing 1276 could also be affixed to the tube 1214 by avariety of methods, including adhesion or a threaded engagement.

[0204] The discharge housing 1276 further comprises a plurality ofoutput channels 1278 for passing the fluid from the discharge chamber1272 into a discharge orifice 1280. The discharge orifice 1280 furthercomprises a threaded portion 1282 to permit a conventional threadedconnector such as a hose nipple 1284 to be threaded into the dischargehousing 1276 for receiving fluid from the discharge aperture 1280. Anoutput end 1285 of the conventional connector 1284 may conveniently becoupled to a variety of fluid receiving devices, such as inhalationmouthpieces, or other structures for receiving a substantially vaporizedflow of the fluid 1130.

[0205] The operation of the embodiment illustrated in FIGS. 1-6 isdescribed below. Liquid, such as fuel, is electronically controlled,metered, and sprayed as an aerosol through the output ports 46 of thefuel injectors 38 into the preliminary mixing chamber 44. While fuel isthe fluid referred to herein, other fluids, such as medicine and wasteliquid may also be vaporized and homogenized using the devices andmethods disclosed.

[0206] As fuel is sprayed into the preliminary mixing chamber 44, thethrottle plate 84 opens to permit an amount of air to be input into theventuri 82. The amount of air permitted to pass by the throttle plate 84is proportional to the amount of fluid sprayed into the preliminarymixing chamber by the output ports 46 of the fuel injectors 38. Anengine-created vacuum pulls the fluid from the mixing chamber 44 throughthe apertures 66 formed in the chamber housing 54.

[0207] When the engine operates, a partial vacuum is produced in theengine intake manifold (not shown). With the throttle plate in a closedposition, the lower pressure air/fuel mixture in the preliminary mixingchamber 44 is drawn tangentially through the apertures 66 into thevortex chamber 64. Specifically, air for the vortex chamber isintroduced through the slot 94 and passes through the ambient airchannel 100 and the conduit 102 into the ambient air conduit 50. Fromthe ambient air conduit 50, ambient air is introduced into thepreliminary mixing chamber where the ambient air mixes with the aerosolfuel prior to entering the apertures 66 as an air/fuel mixture.

[0208] The air/fuel mixture is introduced substantially tangentiallyinto the vortex chamber 64 where the fluid is rotationally accelerateddue to incoming fluid through the apertures 66. The amount of fluidentering the various apertures 66 is substantially equalized by thepresence of the jacket 60. The inside surface 56 of the jacket restrictsthe flow of fluid entering the apertures according to the location ofthe aperture relative to the output port 70, which comprises a lowpressure end of the flow passing through the vortex chamber 64.Essentially, the jacket provides a heightened restriction on aperturescloser to the output port 70 and a lesser, if any, restriction of theapertures farthest from the low pressure end (output port 70).

[0209] Once the fluid is inserted into the vortex chamber 64, the fluidis rotationally accelerated, which causes any non-vaporized particles offluid within the flow to break down into smaller particles, to bevaporized, or both. When the fluid reaches the output port 70, the fluidpasses from the chamber 64 into the intermediate chamber 136 as aspinning column of fluid. In the intermediate chamber 136, the fluid isenfolded upon itself, thus breaking up the spinning column of fluid andcreating additional turbulence and homogenization of the flow.

[0210] The flow is then drawn by the partial vacuum created by theengine manifold through the elongated apertures 106 of the venturi 82.The elongated apertures 106 are significantly larger and more numerousthan conventional small circular venturi chamber apertures as they aredesigned to reduce any pressure drop and to enable a flow of up to 60CFM. In the venturi 82, the ambient air, admitted by the throttle plate84, is mixed with the air/fuel mixture as the air/fuel mixture entersthrough the apertures 106. The ambient air/fuel mixture is furthermixed, and at least partially homogenized, within the venturi 82.

[0211] The partial vacuum of the engine manifold next draws the fluidthrough the centrifuge intake opening 144 as the fluid enters the entrychamber 146. The entry chamber serves to further mix and homogenize thefluid and to direct the fluid into the centrifuge chamber 152tangentially. Specifically, the baffles 150 formed within the entrychamber 146 create a series of tangential passageways 200, 202, and 204through which the fluid is tangentially drawn into the centrifugechamber 152 by the partial engine manifold vacuum.

[0212] In the centrifuge chamber 152, the fluid is rotationallyaccelerated which causes the largest or heaviest particles to be moved,due to their mass, toward the perimeter of the centrifuge chamber 152where these heavier, or more massive, particles collide with theinterior surface 156 and are further broken down and vaporized.

[0213] To reduce the volume of the centrifuge chamber 152, it isadvantageous that the height of the side wall 156 be smaller than theinside diameter 114 of the venturi 82 at the venturi output 110.Additionally, to reduce the volume of the centrifuge chamber 152 and toenhance the centrifugal flow in the chamber 152, the extension member162 extends from the centrifuge housing top wall 160.

[0214] The fluid is then drawn into the four outputs 154 by the enginevacuum. As the lighter particles of the flow centrifugally advancetoward the center of the centrifuge housing 152, they are directed, atan angle, by the conically-shaped portion of the centrifuge contouredtop surface 170 into the apertures 182 formed in the conically-shapedportion 180 and into the four outputs 154. By discharging the fluid fromthe centrifuge chamber in the manner described, a more uniformhydrocarbon distribution is obtained due to the hydrocarbon's generallytendency to be positioned towards the outside of the centrifugal flow inthe centrifuge chamber. In contrast, where only one output port isemployed, the centrifuge discharge is less uniform due to the tendencyof hydrocarbons to be positioned toward the outside of the centrifugalflow.

[0215] Turning now to the embodiment of the invention illustrated inFIG. 7, the vortex configuration 220 is supplied with aerosol fuel byfuel injectors 222. The fuel injectors 222 spray fuel into a preliminarymixing chamber 242. Ambient air is also introduced into the preliminarymixing chamber 242 via the ambient air conduit 244. In the preliminarymixing chamber, the aerosol fuel and the ambient air are mixed so as toenter the vortex chamber 248 through the apertures 260 as an air/fuelmixture.

[0216] In a manner similar to the jacket 60 (FIG. 1), the jacket 272serves as a pressure differential supply to normalize the amount of flowthrough the various apertures 260. The air/fuel mixture enters thevortex chamber 248 through the apertures 216 in a manner similar to thatdescribed in connection with the vortex chamber 54 and aperture 66 ofFIG. 1. As the air/fuel mixture exists the U-shaped output port 340, themixture enters into a mixing chamber 350 prior to entering the vortexchamber 250 through apertures 262. In this configuration, the apertures262 receive the air/fuel mixture exclusively from the output from thevortex chamber 248 to maintain a substantially constant air/fuel ratioas the air/fuel mixture passes through the chambers 248 and 250.

[0217] Subsequently, the air/fuel mixture exits the U-shaped output port242 and enters into mixing chamber 352 prior to entering the vortexchamber 252 through apertures 264. Again, the air/fuel ratio of theair/fuel mixture remains substantially constant as the fluid passesthrough the vortex chambers 250 and 252.

[0218] After exiting the output port 344 of the chamber housing 228, thefluid continues to pass through the mixing chamber 354, apertures 266,and vortex chamber 254 in a manner identical to that described inconnection with the vortex chamber 252. Upon exiting the U-shaped outputport 346, the fluid enters the mixing chamber 356, passes through theapertures 268 into the final chamber 256 prior to exiting the outputport 348.

[0219] By passing through the five chambers 248-256, the fluid becomesincreasingly vaporized and transformed in a gaseous phase as it advancesfrom one chamber to the next. Accordingly, this embodiment permits anair/fuel mixture to pass through several vortex chambers whilemaintaining a substantially constant air/fuel ratio.

[0220] Turning now to the embodiment illustrated in FIGS. 15-17, fuel isinjected into a first chamber 426 from a conventional fuel injector 424.Air is then introduced into the chamber through apertures 436 torotationally accelerate the fluid. As the fluid advances from thechamber 428 to the chamber 430, it passes through a nozzle 490 whichcauses the fluid to undergo additional differentials in pressure toenhance the vaporization of the fluid. The fluid continues to advancethrough the various chambers 430-434 and nozzles 488 and 486. When thefluid reaches the output port 484, it is introduced to an elongatedconduit 478, through which the fluid passes until it reaches the output479.

[0221] To alleviate the problems of acceleration stumble, the elongatedconduit 478 is selectively passed through the chambers 430-434 intodirect communication with the nozzle 490 to selectively isolate thechamber 428 and to permit the fluid to bypass chambers 430-434.

[0222] When accelerating, the solenoid 476 is energized, which causesthe conduit base 480 to slide along the interior surface 466 of the tubeportion 456, compressing the spring 482 and advancing the bypass conduit478 into direct communication with the chamber 428. In most instances,the period of insertion will be on the order of 0.5 seconds.

[0223] After the fluid has exited the output 479, it enters the venturi506 and is passed into the centrifuge chamber through the output channel532. Then, after spinning centrifugally in the centrifuge chamber 542,the fluid is discharged through output 548 into the engine manifold (notshown).

[0224] The embodiment illustrated in FIG. 20 permits the effectivecross-sectional area of the output 660 to be selectively varied. Inoperation, the stepper motor advances and retracts the conical plug 678relative to the output 660. Thus, as the conical plug is moved relativeto the output, the effective cross-sectional area of the output may beselectively varied.

[0225] An alternate embodiment of a vortex chamber housing isillustrated in FIG. 23. In operation, the vortex chamber housing 940receives fluid through the tangential slots 950 into the chamberinterior 952 to create a vortical flow of fluid within the chamberinterior 952. The elongated slots 950 introduce the fluid tangentiallyinto the chamber interior as a sheet of fluid along the interior surface946 of the vortex chamber housing to prevent liquid particles fromcongregating on the interior surface 946. As the fluid spins vorticallywithin the chamber 952, the pressure differentials and the overallturbulence of the flow within the chamber 952 cause the fluid to bevaporized and homogenized.

[0226]FIGS. 24 and 25 illustrate an alternative embodiment of a venturi956 formed in accordance with the principles of the present invention.In operation, the venturi 956 receives a flow of fluid through theventuri inlet opening 962. This flow of fluid is then mixed with anair/fuel mixture which enters the venturi interior 960 throughtangential apertures 958 formed in the wall 956 to create a helical flowof fluid through the venturi 954. Introducing the air/fuel mixturetangentially into the venturi interior 960 causes the flow through theventuri 954 to spin helically. Advantageously, the air/fuel mixture isintroduced in the narrow throat portion 959 of the venturi interior 960because the narrow throat portion 959 comprises the region of fastestair flow within the venturi 954. By creating a helical flow of fluidthrough the venturi 956, the turbulence, and thus the vaporization andhomogenization, of the fluid is substantially enhanced.

[0227] FIGS. 26-30 illustrate a yet additional embodiment of acentrifugal vortex system 970. As shown in FIGS. 27 and 28, in thisembodiment, fuel is sprayed into the preliminary mixing chamber 976 bythe fuel injectors 974. The air/fuel mixture is then tangentiallyintroduced to the vortex chamber 990 through an array of tangentialapertures 992 formed in the vortex chamber housing 978. The air/fuelmixture is then output through output port 994.

[0228] When the engine is at idle, the secondary throat 977 issubstantially sealed by the conical plug 1012 being engaged with theaperture 1010. Additionally, the secondary throttle plate 1032 (FIG. 29)is in a closed position. Further, while the engine is at idle, theprimary conical plug 1000 is raised a distance above the aperture 996 soas to permit a small flow of the air/fuel mixture to pass from theoutput port 994 into the primary throat 973. At idle, the primarythrottle plate 1030 (FIG. 29) is closed. Then, as the engine speed isincreased from idle, the primary linear actuator 978 moves the conicalplug away from the aperture 996 to permit a greater amount of air/fuelmixture to pass through the aperture 996 into the primary throat 973.Simultaneously, the primary throttle plate 1030 begins to open toincrease the amount of air/fuel mixture admitted to the engine.

[0229] With reference to FIGS. 26 and 30, as the primary throttle plate1030 continues to open, the primary arm 1044 rotates in a clockwisedirection causing the link 1046 to advance through the slot 1052 formedin the secondary arm 1048. When the primary throttle plate 1032 has beenopened to a predetermined position, such as approximately 40% open, thelink 1046 contacts the end 1054 of the slot 1052 and the link 1046begins to cause the secondary arm 1048 to rotate. The rotation of thesecondary arm 1048 then begins to open the secondary throttle plate 1032by rotating the shaft 1036.

[0230] Simultaneously with the opening of the secondary throttle plate1032, the secondary linear actuator 981 disengages the conical plug 1012from the aperture 1010 to permit flow through the passageway 1111. Thus,as the primary throttle plate 1030 continues to open past thepredetermined position, the secondary throttle plate 1032 opens and thepassageway 1111 is opened to allow flow through both the primary andsecondary throats 973 and 977 to enhance the volumetric efficiency ofthe system 970.

[0231] As the primary throttle plate 1030 continues to open, the linkageassembly 1042 continues to cause the secondary throttle plate to opensuch that when the primary throttle plate 1030 is fully open, thesecondary throttle plate 1032 is also fully open. When the primary andsecondary throttle plates 1030 and 1032 are fully open, the conicalplugs 1000 and 1012 are fully retracted to maximize the flow through theprimary and secondary throats 973 and 977 to enhance volumetricefficiency. Then, as the engine speed is decreased, the primary throttleplate 1032 begins to close, thus causing the secondary throttle plate1032 to also begin to close. As the secondary throttle plate begins toclose, the conical plug 1012 is moved closer to the aperture 1010 torestrict fluid flow through the passageway 1111 into the secondarythroat 977. When the primary throttle plate 1030 is repositioned at thepredetermined location, the secondary throttle plate is completelyclosed and the conical plug 1012 is reinserted within the aperture 1010to seal off the secondary throat 977 and to isolate the primary throat973, thus providing a high resolution response. As the engine speed isfurther decreased toward idle, the flow through the primary throat 973is further reduced by continuing to close the primary throttle plate1030 and moving the primary conical plug 1000 into close proximity withthe aperture 996.

[0232] Thus, in the configuration illustrated in FIGS. 26-30, both highresolution response and volumetric efficiency are attainable. The highresolution response is achieved at low engine speeds by isolating theflow within the primary throat 973. At high engine speeds, wherevolumetric efficiency is desirable, the secondary throat 977 is openedand used in combination with the primary throat 973.

[0233]FIG. 31 illustrates an embodiment similar to that illustrated inFIGS. 26-30 and described above. The primary difference between theembodiment illustrated in FIG. 31 and that illustrated in FIGS. 26-30 isthat the embodiment of FIG. 31 is designed for a four barrel systemwhereas the embodiment illustrated in FIGS. 26-30 is intended for a twobarrel system.

[0234] In operation, the embodiment illustrated in FIG. 31 receives anair/fuel mixture into the primary and secondary throats from the vortexchamber assemblies 1060 and 1062 in a manner identical to that describedabove in the embodiment illustrated in FIGS. 26-30. The embodiment ofFIG. 31 operates essentially in the same manner as the embodimentillustrated in FIGS. 26-30 except that there are two secondary throatsand two primary throats instead of only one primary and secondary throatas illustrated in FIGS. 26-30.

[0235] The linkage assembly 1100 illustrated in FIG. 31 is configuredand operates in a manner identical to that of the linkage assembly 1042illustrated in FIGS. 26 and 30. The primary shaft 1090 controls theprimary throttle plates 1080 and 1082 and the secondary shaft 1094controls the throttle plates 1084 and 1086. In a manner similar to thatillustrated in FIGS. 26-30 and described above, as the primary throttleplates 1080 and 1082 are opened, the primary linear actuators moveconical plugs within the primary throats to permit a flow of fluidthrough each primary throat. Then, as the linkage assembly 1100 causesthe secondary throttle plates 1084 and 1086 to open, the secondarylinear actuators 1068 and 1070 move conical plugs within the secondarythroats to permit fluid to flow through the primary and secondarythroats to enhance volumetric efficiency. Likewise, as the throttleplates close, the respective linear actuators also move the conicalplugs to enhance a high resolution response.

[0236] As discussed above, FIGS. 32 and 33 illustrate a yet additionalembodiment of the invention. In this embodiment, positive pressure isprovided into the system 1120 through a positive pressure source 1124which delivers gas, under pressure, into the venturi inlet opening 1180and into the pressurized gas conduit 1178. The pressurized gas passesthrough the pressurized gas conduit 1178 into the pressure chamber 1164.As the pressure within the pressure chamber 1164 increases due to thepressurized gas, the compressible container 1122 is compressed, thusreducing the volume and increasing the pressure of the container ofhollow interior 1144. As the compressible container 1122 is compressed,the fluid 1130 within the container 1122 is forced out of the container1122 through the output port 1160, through the passageway 1159, and intothe fluid conduit 1132.

[0237] The flow of fluid from the fluid conduit 132 to the conduit 134is controlled by the regulator 1184. In the biased position illustratedin FIG. 33, the sphere 1188 is biased against the spherical seat 1194 toprevent fluid from flowing from the conduit 1132 to the conduit 1134. Asthe pressure within the conduit 1132 increases, however, the biasagainst the spherical seat 1194 is overcome and the sphere 1188 isdislodged from the spherical seat 1194 to permit the fluid to pass fromthe conduit 1132 to the conduit 1134.

[0238] The bias of the sphere 1188 against the spherical seat 1194 canbe adjusted by advancing or withdrawing the screw 1190 within thehousing 1186. As the screw 1190 is advanced into the housing 1186, thespring 1192 is compressed, thus increasing the bias on the sphere 1188.Conversely, as the screw 1190 is withdrawn from within the housing 1186,the spring 1192 is decompressed, thus reducing the amount of bias on thesphere 1188. With a reduced bias on the sphere 1188, a lesser pressurein the conduit 1132 is required to unseat the sphere 1188 and to enableflow from the conduit 1132 to the conduit 1134.

[0239] After passing by the regulator 1184, the fluid passes through theconduit 1134 and enters the venturi throat portion 1198 as an aerosol.As the pressurized gas passes through the venturi 1126, the velocity ofthe gas increases as it passes through the narrow throat portion 1198,thus creating a low pressure region at the narrow throat portion 1198.The low pressure associated with the high velocity flow through theventuri narrow throat portion 1198 helps to draw the fluid through theconduit 1134 into the narrow throat portion 1198.

[0240] In the venturi throat portion 1198, pressurized gas from thesource of pressurized gas 1124 is mixed with the fluid 1130. Aftermixing with the pressurized gas, the fluid exits the venturi 1126through the venturi outlet opening 1196 as an aerosol. From the venturioutlet opening 1196, the fluid passes through apertures 1202 formed inthe boss extension 1204 and into the mixing chamber 1200. From themixing chamber 1200, fluid enters the vortex chamber 1224 through thetangential slots 1222 to create a vortical flow within the vortexchamber 1224 for breaking down into smaller particles and vaporizing anynon-vaporized particles in the vortical flow.

[0241] The fluid then passes from the vortex chamber 1224 into themixing chamber 1232 through the apertures 1242 formed in the outputfixture 1230. The fluid continues to pass through the subsequent vortexchamber housings 1244, 1248, 1250, 1254, 1256, and 1258 as well asthrough subsequent output fixtures 1246, 1260, 1262, 1264, 1266, 1268,and 1270 in the same manner as the fluid passes through the vortexchamber housing 1128 and the output fixture 1230 respectively. The fluidis further homogenized and vaporized through each succeeding vortexchamber housing.

[0242] Upon exiting the final output fixture 1270, the fluid passesthrough a discharge chamber 1272 and into the channels 1270 to supplythe output orifice 1280 with a supply of substantially vaporized fluid.To facilitate the delivery of the vaporized fluid to its finaldestination, the fluid may pass through a conventional hose connector1284.

[0243] The various systems and methods described have been directed tothe vaporization and homogenization of fuel for internal and externalcombustion engines. The inventor appreciates that the devices andmethods disclosed in this document have applicability in connection withthe preparation of other fluids. For example, the present systems anddevices may be employed in connection with preparing a medication to beadministered to a patient by inhalation through the lungs into thebloodstream. In the past, it has been difficult to sufficiently breakdown and vaporize a medication into particles small enough to passdirectly into the bloodstream through a patient's lungs. The systems andmethods disclosed in this document have applicability in alleviatingthat need.

[0244] The systems and methods disclosed in this documents are alsoapplicable and useful in the breakdown, vaporization, and homogenizationof waste fluids for incineration and waste management. As the wastefluid particles are broken down into extremely small particle sizes, thewaste fluid introduced into an incinerator will be burned moreefficiently, thereby minimizing pollution and increasing the efficiencyof which the waste fluids are incinerated.

[0245] In compliance with the statute, the invention has been describedin language more or less specific as to structural and methodicalfeatures. It is to be understood, however, that the invention is notlimited to the specific features shown and described, since the meansherein disclosed comprise preferred forms of putting the invention intoeffect. The invention is, therefore, claimed in any of its forms ormodifications with the proper scope of the appended claims appropriatelyinterpreted in accordance with the doctrine of equivalents.

1. A centrifugal vortex system for vaporizing a fluid, comprising: achamber housing defining at least one vortex chamber for creating avortical flow of fluid; a chamber output coupled to the vortex chamberfor discharging fluid from the vortex chamber; an array of aperturesformed in the chamber housing to allow the input of fluid tangentiallyinto the vortex chamber to create a turbulent vortical flow through thevortex chamber for breaking down into smaller particles and vaporizingany non-vaporized particles in the vortical flow; wherein the array ofapertures comprises a plurality apertures arranged in rows and aplurality of apertures arranged in columns, the apertures being formedin the chamber housing about the vortex chamber to enhance theturbulence of the vortical flow of the fluid through the chamber.
 2. Acentrifugal vortex system according to claim 1 wherein the plurality ofcolumns are staggered to enhance the turbulence of the vortical flow ofthe fluid through the chamber.
 3. A centrifugal vortex system accordingto claim 1 wherein the plurality of rows are staggered to enhance theturbulence of the vortical flow of the fluid through the chamber.
 4. Acentrifugal vortex system according to claim 1 wherein the chamberhousing has an inner chamber wall, further comprising: a plurality ofsteps formed on the inner chamber wall to increase the turbulence of avortical flow within the vortex chamber and to break down into smallerparticles any non-vaporized particles in the vortical flow to enhancethe vaporization of the non-vaporized particles.
 5. A centrifugal vortexsystem according to claim 1 wherein the chamber housing has an innerchamber wall, further comprising: a textured surface formed on the innerchamber wall to increase the turbulence of a vortical flow within thevortex chamber and to break down into smaller particles anynon-vaporized particles in the vortical flow to enhance the vaporizationof the non-vaporized particles.
 6. A centrifugal vortex system accordingto claim 1, further comprising: a pressure differential supplyassociated with the input apertures to allow a differential pressure offluid at the input apertures according to the location of the apertures.7. A centrifugal vortex system for vaporizing a fluid, comprising: afirst chamber housing defining a first vortex chamber and a secondchamber housing defining a second vortex chamber, the second vortexchamber coupled to the first vortex chamber; a plurality of inputapertures formed in each chamber housing to allow air and a second fluidto be input tangentially into each vortex chamber; a first vortexchamber output coupled to the input apertures formed in the secondvortex chamber; the input apertures of the second vortex chamberreceiving an air-second fluid mixture exclusively from the first vortexchamber output to maintain a substantially constant air-second fluidratio as the air-second fluid mixture passes through the first andsecond vortex chambers.
 8. A centrifugal vortex system according toclaim 7, further comprising: a third chamber housing defining a thirdvortex chamber, the third vortex chamber coupled to the second vortexchamber; a plurality of input apertures formed in each chamber housingto allow air and a second fluid to be input tangentially into the thirdvortex chamber; a second vortex chamber output coupled to the inputapertures formed in the third vortex chamber; the input apertures of thethird vortex chamber receiving an air-second fluid mixture exclusivelyfrom the second vortex chamber output to maintain a substantiallyconstant air-second fluid ratio as the air-second fluid mixture passesthrough the second and third vortex chambers.
 9. A centrifugal vortexsystem according to claim 7, further comprising: a third chamber housingdefining a third vortex chamber and a fourth chamber housing defining afourth vortex chamber, the third vortex chamber coupled to the secondvortex chamber and the fourth vortex chamber coupled to the third vortexchamber; a plurality of input apertures formed in each chamber housingto allow air and a second fluid to be input tangentially into the thirdand fourth vortex chambers; a second vortex chamber output coupled tothe input apertures formed in the third vortex chamber and a thirdvortex chamber output coupled to the input apertures formed in thefourth vortex chamber; the input apertures of the third vortex chamberreceiving an air-second fluid mixture exclusively from the second vortexchamber output to maintain a substantially constant air-second fluidratio as the air-second fluid mixture passes through the second andthird vortex chambers; the input apertures of the fourth vortex chamberreceiving an air-second fluid mixture exclusively from the third vortexchamber output to maintain a substantially constant air-second fluidratio as the air-second fluid mixture passes through the third andfourth vortex chambers.
 10. A centrifugal vortex system according toclaim 7, further comprising: a pressure differential supply associatedwith the input apertures formed in the first vortex housing to allow adifferential pressure of fluid at the input apertures according to alocation of the apertures.
 11. A vortex system for vaporizing a fluid,comprising: a vortex housing defining a vortex chamber comprising aninner chamber wall; a plurality of input apertures formed in the vortexhousing to allow the input of fluid into the vortex chamber; a pluralityof steps formed on the inner chamber wall to increase the turbulence ofa vortical flow within the vortex chamber and to break down into smallerparticles any non-vaporized particles in the vortical flow to enhancethe vaporization of the non-vaporized particles.
 12. A vortex system forvaporizing a fluid according to claim 11 wherein the inner chamber wallfurther comprises a textured surface.
 13. A vortex system for vaporizinga fluid according to claim 11 wherein each step comprises a ramp surfaceand a transverse surface, further comprising: a plurality of aperturesformed on each step transverse surface for inputting fluid into thevortex chamber.
 14. A vortex system for vaporizing a fluid, comprising:a vortex housing defining a vortex chamber comprising an inner chamberwall; a plurality of input apertures formed in the vortex housing toallow the input of fluid into the vortex chamber; a textured surfaceformed on the inner chamber wall to increase the turbulence of avortical flow within the vortex chamber and to break down into smallerparticles any non-vaporized particles in the vortical flow to enhancethe vaporization of the non-vaporized particles.
 15. A vortex system forvaporizing a fluid according to claim 14 wherein the plurality of inputapertures are arranged in a plurality of rows and a plurality ofcolumns.
 16. A vortex system for vaporizing a fluid according to claim14, further comprising: a plurality of steps formed on the inner chamberwall to increase the turbulence of a vortical flow within the vortexchamber and to break down into smaller particles any non-vaporizedparticles in the vortical flow to enhance the vaporization of thenon-vaporized particles.
 17. A centrifugal vortex system for vaporizinga fluid, comprising: a fluid flow path having a high pressure end and alow pressure end; a vortex housing defining a vortex chamber throughwhich a fluid flow is directed, the vortex chamber being positionedalong the fluid flow path and interposed between the high pressure endand the low pressure end to permit a fluid to flow from the highpressure end to the low pressure end; a plurality of input aperturesformed in the vortex housing to allow the input of fluid tangentiallyinto the vortex chamber for vaporizing the fluid; wherein the aperturesare located at different distances relative to the low pressure end; apressure differential supply associated with the input apertures toallow a differential pressure of fluid at the input apertures accordingto the location of the apertures relative to the low pressure end.
 18. Avortex system for vaporizing a fluid according to claim 17 wherein theplurality of input apertures are arranged in a plurality of rows and aplurality of columns.
 19. A vortex system for vaporizing a fluidaccording to claim 17 wherein the pressure differential supply comprisesa jacket.
 20. A vortex system for vaporizing a fluid according to claim17 wherein the pressure differential supply comprises a jacket having anincreasing diameter inner surface.
 21. A vortex system for vaporizing afluid according to claim 17 wherein the pressure differential supplycomprises a jacket having a tapered inner surface.
 22. A vortex systemfor vaporizing a fluid according to claim 17 wherein the pressuredifferential supply comprises a jacket having an inner surface, thejacket inner surface defining a variable width gap between the jacketinner surface and a vortex housing exterior surface.
 23. A vortex systemfor vaporizing a fluid according to claim 17 wherein the pressuredifferential supply comprises a jacket having a variable diameter innersurface, the inner surface having a maximum diameter end and a minimumdiameter end; wherein the minimum diameter end is positioned adjacent toan aperture closer to the low pressure end to reduce a tendency of theaperture closer to the low pressure end to receive more flow than anaperture located farther from the low pressure end.
 24. A centrifugalvortex system for vaporizing a fluid, comprising: a vortex chamberhousing defining at least one vortex chamber; a vortex chamber outputcoupled with the vortex chamber to discharge flow from the vortexchamber; an array of apertures formed in the chamber housing to allowthe input of air tangentially into the vortex chamber to create avortical flow through the vortex chamber for breaking down into smallerparticles any non-vaporized particles in the vortical flow; a centrifugehousing for homogenizing the vortical flow, the centrifuge housingcomprising: an entry chamber in fluid communication with the vortexchamber output; a centrifuge chamber coupled to the entry chamber; aseries of baffles positioned within the entry chamber for inputting thefluid tangentially into the centrifuge chamber to enhance thevaporization of the fluid.
 25. A centrifugal vortex system according toclaim 24 wherein the baffles are tangentially oriented relative to thecentrifuge chamber.
 26. A centrifugal vortex system according to claim24 wherein the centrifuge chamber further comprises a textured innersurface to enhance the vaporization of the fluid.
 27. A centrifugalvortex system for vaporizing a fluid, comprising: a first chamberhousing having a first vortex chamber; a second chamber housing having asecond vortex chamber, the first vortex chamber having a first vortexchamber output coupled to the second vortex chamber to permit a fluid toflow between the first and second vortex chambers; a second chamberoutput coupled with the second vortex chamber; a plurality of inputapertures formed in the first chamber housing and in the second chamberhousing to allow the input of fluid tangentially into each vortexchamber; an elongated bypass conduit selectively insertable through thesecond chamber housing output into the first housing output to isolatefluid flow in the first chamber and to permit the fluid to bypass thesecond chamber.
 28. A centrifugal vortex system according to claim 27,further comprising: a base attached to the elongated bypass conduit; atube, the base being positioned within the tube; a solenoid formedaround the tube to cause the base to travel within the tube forselectively advancing the bypass conduit into the first housing input; abias member coupled with the base to bias the bypass conduit away fromthe first chamber housing.
 29. A centrifugal vortex system according toclaim 27, further comprising: a base attached to the elongated bypassconduit; a tube, the base being slidingly positioned within the tube; asolenoid formed around the tube to cause the base to travel within thetube for selectively advancing the bypass conduit into the first housinginput; a spring member coupled with the base to bias the bypass conduitaway from the first chamber housing.
 30. A centrifugal vortex systemaccording to claim 27, further comprising: a tube, the bypass conduitbeing positioned within the tube; a solenoid formed around the tube toselectively cause the bypass conduit to travel within the tube intoassociation with the first housing input.
 31. A centrifugal vortexsystem for vaporizing a fluid, comprising: a chamber housing defining atleast one vortex chamber; a chamber output coupled with the vortexchamber for discharging flow from the vortex chamber; an array ofapertures formed in the chamber housing to allow the input of airtangentially into the vortex chamber to create a vortical flow throughthe vortex chamber for breaking down into smaller particles anynon-vaporized particles in the vortical flow; an adjustablecross-sectional area output port in fluid communication with the chamberoutput for regulating a flow of fluid through the vortex chamber, theoutput port comprising: a conduit in fluid communication with the vortexchamber output; a seat positioned within the conduit; a plug sized toengage the conical seat; an actuator coupled with the plug toselectively move the plug relative to the seat to selectively adjust thecross-sectional area of the output port.
 32. A centrifugal vortex systemaccording to claim 31 wherein the actuator comprises a stepper motor.33. A centrifugal vortex system according to claim 31 wherein the arrayof apertures are oriented in a plurality of rows and a plurality ofcolumns.
 34. A centrifugal vortex system for vaporizing a fluid,comprising: a chamber housing defining at least one vortex chamber; achamber output coupled with the vortex chamber to discharge flow fromthe vortex chamber; an array of apertures formed in the chamber housingto allow the input of air tangentially into the vortex chamber to createa vortical flow through the vortex chamber for breaking down intosmaller particles any non-vaporized particles in the vortical flow; acentrifuge housing for homogenizing the fluid, the centrifuge housingcomprising: an intake opening in fluid communication with the vortexchamber output; a centrifuge chamber coupled to the intake opening, thecentrifuge chamber defined by a top surface, a bottom surface, and aside surface; a plurality of output conduits coupled to the centrifugechamber for discharging the fluid from the centrifuge chamber in asubstantially homogeneous mixture.
 35. A centrifugal vortex systemaccording to claim 34 wherein the centrifuge chamber side surfacecomprises a textured surface.
 36. A centrifugal vortex system accordingto claim 34, wherein the array of apertures are oriented in a pluralityof rows and a plurality of columns.
 37. A centrifugal vortex systemaccording to claim 34 wherein the bottom surface further comprises aconically shaped portion surrounding the output conduits for directingthe fluid into the output conduits.
 38. A centrifugal vortex systemaccording to claim 34, further comprising an extension member positionedcentrally on the top surface and extending from the top surface towardthe bottom surface to enhance a centrifugal flow of the fluid in thecentrifuge housing and reduce the volume of the centrifuge chamber. 39.A centrifugal vortex system for vaporizing a fluid, comprising: achamber housing defining at least one vortex chamber; a chamber outputcoupled with the vortex chamber to discharge flow from the vortexchamber; an array of apertures formed in the chamber housing to allowthe input of air tangentially into the vortex chamber to create avortical flow through the vortex chamber for breaking down into smallerparticles any non-vaporized particles in the vortical flow; a centrifugehousing for homogenizing the fluid, the centrifuge housing comprising: acentrifuge chamber in fluid communication with the chamber output, thecentrifuge chamber having a volume defined by a top surface, a bottomsurface, and a side surface; an output conduit formed on the centrifugechamber bottom surface, the output conduit coupled to the centrifugechamber for discharging fluid from the centrifuge chamber; an extensionmember positioned centrally on the top surface and extending from thetop surface toward the bottom surface to enhance a centrifugal flow ofthe fluid in the centrifuge housing and reduce the volume of thecentrifuge chamber.
 40. A centrifugal vortex system according to claim39 further comprising a plurality of output conduits formed on thecentrifuge chamber bottom surface coupled to the centrifuge chamber fordischarging fluid from the centrifuge chamber.
 41. A centrifugal vortexsystem according to claim 39 wherein the bottom surface furthercomprises a conically shaped portion surrounding the output conduits fordirecting the fluid into the output conduits.
 42. A centrifugal vortexsystem for vaporizing a fluid, comprising: a chamber housing defining atleast one vortex chamber; a chamber output coupled with the vortexchamber to discharge flow from the vortex chamber; an array of aperturesformed in the chamber housing to allow the input of air tangentiallyinto the vortex chamber to create a vortical flow through the vortexchamber for breaking down into smaller particles any non-vaporizedparticles in the vortical flow; a venturi in fluid communication withthe chamber output, the venturi having a maximum inside diameter and aminimum inside diameter; a centrifuge housing for homogenizing thefluid, the centrifuge housing comprising: an intake opening in fluidcommunication with the venturi; a centrifuge chamber coupled to theintake opening, the centrifuge chamber having a volume defined by a topsurface, a bottom surface, and a substantially circular cross-sectionalside wall inside surface, the side wall inside surface having a diameterand a height; wherein the height of the side wall inside surface issmaller than the venturi maximum inside diameter to enhance a flow offluid from the venturi through the centrifuge chamber and to reduce thevolume of the centrifuge chamber.
 43. A centrifugal vortex systemaccording to claim 42 further comprising a plurality of output conduitsformed on the centrifuge chamber bottom surface coupled to thecentrifuge chamber for discharging fluid from the centrifuge chamber.44. A centrifugal vortex system according to claim 42 wherein the bottomsurface further comprises a conically shaped portion surrounding theoutput conduits for directing the fluid into the output conduits.
 45. Acentrifugal vortex system for vaporizing a fluid, comprising: a chamberhousing having a chamber housing input and a chamber housing output; aplurality of vortex chambers interposed between the chamber housinginput and the chamber housing output; an array of apertures formed inthe chamber housing to allow the input of air tangentially into a vortexchamber to create a vortical flow through the vortex chamber forbreaking down into smaller particles any non-vaporized particles in thevortical flow; wherein the vortex chamber has a maximum inside diameter;wherein a vortex chamber adjacent to the chamber housing input has asmaller maximum inside diameter than the chamber adjacent to the chamberhousing output to prevent the chamber adjacent to the chamber housingoutput from receiving more flow than the chamber adjacent to the chamberhousing input.
 46. A centrifugal vortex system according to claim 45,further comprising a nozzle positioned in at least one of the vortexchambers for creating an additional pressure differential for enhancingthe vaporization of any non-vaporized particle in the flow.
 47. Acentrifugal vortex system according to claim 45, further comprising apressure supply associated with the apertures to allow a differentialpressure of fluid at the apertures according to the location of theapertures.
 48. A centrifugal vortex system according to claim 45,further comprising a jacket having an inner surface, the jacket innersurface defining a variable width gap between the jacket inner surfaceand a vortex housing exterior surface.
 49. A centrifugal vortex systemaccording to claim 45, further comprising: a jacket having an innersurface, the jacket inner surface defining a variable width gap betweenthe jacket inner surface and a vortex housing exterior surface; a bypassconduit insertable through a vortex chamber to allow the fluid toselectively bypass the vortex chamber.
 50. A centrifugal vortex systemfor vaporizing a fluid, comprising: a chamber housing defining at leastone vortex chamber; a chamber output coupled with the vortex chamber todischarge flow from the vortex chamber; an array of apertures formed inthe chamber housing to allow the input of air tangentially into thevortex chamber to create a vortical flow through the vortex chamber forbreaking down into smaller particles any non-vaporized particles in thevortical flow; a venturi in fluid communication with the chamber output,the venturi having a minimum inside diameter; a centrifuge housing forhomogenizing the fluid, the centrifuge housing comprising: a centrifugechamber in fluid communication with the venturi, the centrifuge chamberhaving a top surface, a bottom surface, and an output aperture formed inthe bottom surface to allow fluid to be discharged from the centrifugehousing, the output aperture having an inside diameter; wherein theratio of the output aperture inside diameter to the venturi minimuminside diameter is approximately 1.66:1 to enhance the vacuum pressureat the output aperture.
 51. A method of vaporizing a fluid, comprisingthe steps of: providing a preliminary mixing chamber; introducing anaerosol into the mixing chamber; introducing air into the mixingchamber; mixing the aerosol and the air in the preliminary mixingchamber to form an aerosol-air mixture; providing a first vortexchamber; introducing the aerosol-air mixture tangentially into the firstvortex chamber to create a vortical flow and to break down into smallerparticles any non-vaporized particles in the aerosol-air mixture.
 52. Amethod of vaporizing a fluid according to claim 51, further comprisingthe steps of: vortically spinning the fluid in a first spin direction inthe first vortex chamber; providing a second vortex chamber; introducingthe fluid into a second portion of the flow path; adding turbulence tothe flow path by changing the spin direction of the fluid by causing thefluid to spin in a second spin direction in the second vortex chamber;wherein the second spin direction is substantially opposite from thefirst spin direction.
 53. A method of vaporizing a fluid, comprising thesteps of: providing a first vortex chamber; introducing a fluid into thefirst vortex chamber; vertically spinning the fluid in a first spindirection in the first vortex chamber; providing a second vortexchamber; introducing the fluid into a second portion of the flow path;adding turbulence to the flow path by changing the spin direction of thefluid by causing the fluid to spin in a second spin direction in thesecond vortex chamber; wherein the second spin direction issubstantially opposite from the first spin direction.
 54. A method ofvaporizing a fluid, comprising the steps of: providing a preliminarymixing chamber; introducing an aerosol into the mixing chamber;introducing air into the mixing chamber; mixing the aerosol and the airin the preliminary mixing chamber to form an aerosol-air mixture;providing a first vortex chamber; introducing the aerosol-air mixturetangentially into the first vortex chamber to create a vortical flow andto break down into smaller particles any non-vaporized particles in theaerosol-air mixture.
 55. A centrifugal vortex system for vaporizing afluid, comprising: a first chamber housing defining a first vortexchamber and a second chamber housing defining a second vortex chambercoupled with the first vortex chamber; a plurality of input aperturesformed in each chamber housing to allow the input of fluid tangentiallyinto each vortex chamber; an output coupled with each vortex chamber;wherein the input apertures of the first vortex chamber are oriented totangentially receive fluid in a first direction; wherein the inputapertures of the second vortex chamber are oriented to tangentiallyreceive fluid in a second direction; wherein the first direction issubstantially opposite from the second direction.
 56. A centrifugalvortex system for vaporizing a fluid, comprising: a chamber housingdefining at least one vortex chamber; a chamber output coupled with thevortex chamber to discharge flow from the vortex chamber; an array ofapertures formed in the chamber housing to allow the input of airtangentially into the vortex chamber to create a vortical flow throughthe vortex chamber for breaking down into smaller particles anynon-vaporized particles in the vortical flow; a centrifuge housing forhomogenizing the fluid in a turbulent flow, the centrifuge housingcomprising: an intake opening in fluid communication with the chamberoutput; a centrifuge chamber coupled to the intake opening, thecentrifuge chamber having an inside surface; wherein the inside surfaceis textured to enhance the turbulent flow through the centrifuge and tobreak down into smaller particles, spread, and enhance evaporation ofany non-vaporized particles that collide with the inside surface.
 57. Acentrifugal vortex system according to claim 56 wherein the vortexchamber has a textured inner wall for enhancing the turbulent flowthrough the vortex chamber.
 58. A centrifugal vortex system forvaporizing a fluid, comprising: a chamber housing defining at least onevortex chamber; a chamber output coupled with the vortex chamber todischarge flow from the vortex chamber; an array of apertures formed inthe chamber housing to allow the input of air tangentially into thevortex chamber to create a vortical flow through the vortex chamber forbreaking down into smaller particles any non-vaporized particles in thevortical flow; a centrifuge housing for homogenizing the fluid, thecentrifuge housing comprising: a centrifuge chamber in fluidcommunication with the chamber output, the centrifuge chamber having atop surface, a bottom surface, and a centrifuge output formed in thebottom surface for discharging fluid from the centrifuge housing;wherein a portion of the centrifuge chamber bottom surface adjacent toand surrounding the centrifuge output is substantially conically shapedto facilitate the direction of the fluid into the centrifuge output. 59.A centrifugal vortex system according to claim 58, further comprising anextension member positioned centrally on the centrifuge chamber topsurface and extending from the top surface toward the bottom surface toenhance a centrifugal flow of the fluid in the centrifuge housing and toreduce the volume of the centrifuge chamber.
 60. A centrifugal vortexsystem according to claim 58 wherein the chamber output furthercomprising a plurality of output conduits formed on the centrifugechamber bottom surface coupled to the centrifuge chamber for dischargingfluid from the centrifuge chamber.
 61. A centrifugal vortex systemaccording to claim 58, further comprising: a linear actuator coupled toa plug, the linear actuator being positioned adjacent to the chamberoutput so that the linear actuator may selectively vary a position ofthe plug relative to the chamber output to vary an amount of flowresistance through the chamber output; wherein the linear actuator andthe chamber output are substantially coaxial.
 62. A centrifugal vortexsystem according to claim 58, further comprising: a centrifuge chamberinput for inputting fluid into the centrifuge chamber; an extension armpositioned within the centrifuge housing, wherein the extension arm ispositioned adjacent to the centrifuge chamber input to prevent fluidwithin the centrifuge chamber from re-entering the centrifuge chamberinput.
 63. A centrifugal vortex system for vaporizing a fluid,comprising: a vortex chamber housing defining a vortex chamber forcreating a vortical flow of fluid; a chamber output coupled to thevortex chamber housing for discharging fluid from the vortex chamber; aprimary throat in fluid communication with the chamber output forreceiving fluid from the chamber output; a secondary throat in fluidcommunication with the primary throat for receiving fluid from theprimary throat; a primary plug removably positioned between the vortexchamber output and the primary throat to selectively restrict fluid flowbetween the vortex chamber and the primary throat; a secondary plugremovably positioned between the primary throat and the secondary throatto selectively restrict fluid flow between the primary throat and thesecondary throat.
 64. A centrifugal vortex system according to claim 63,further comprising: a primary linear actuator coupled to the primaryplug for selectively positioning the primary plug between the vortexchamber output and the primary throat; a secondary linear actuatorcoupled to the secondary plug for selectively positioning the secondaryplug between the primary throat and the secondary throat.
 65. Acentrifugal vortex system according to claim 63, further comprising: aprimary throttle plate positioned within the primary throat forcontrolling the amount of fluid flow through the primary throat; asecondary throttle plate positioned within the secondary throat forcontrolling the amount of fluid flow through the secondary throat; alinkage assembly secured between the primary throttle plate and thesecondary throttle plate to move the secondary throttle plate inresponse to motion of the primary throttle plate.
 66. A centrifugalvortex system according to claim 63, further comprising: a primarythrottle plate positioned within the primary throat for controlling theamount of fluid flow through the primary throat; a secondary throttleplate positioned within the secondary throat for controlling the amountof fluid flow through the secondary throat; a linkage assembly securedbetween the primary throttle plate and the secondary throttle plate tomove the secondary throttle plate in response to motion of the primarythrottle plate; wherein the linkage assembly further comprises: aprimary arm coupled to the primary throttle plate; a secondary armcoupled to the secondary throttle plate; a link interconnecting theprimary arm to the secondary arm so that as the primary arm rotates inresponse to movement of the primary throttle plate, the primary armmoves the link to impart motion to the secondary arm.
 67. A centrifugalvortex system according to claim 63 wherein: the primary throat has amaximum cross-sectional area; the secondary throat has a maximumcross-sectional area greater than the cross-sectional area of theprimary throat.
 68. A venturi for mixing two fluids, comprising: aventuri housing having an intake opening for receiving a first fluid, anoutput opening for discharging a flow of fluid, an outside surface andan inside surface, the inside surface defining a hollow interiorextending between the intake opening and the output opening; a pluralityof tangential apertures formed in the venturi housing between the intakeopening and the output opening for introducing a second fluid into thehollow interior tangentially to mix the first and second fluids bycreating a helical flow of fluid within the hollow interior.
 69. Acentrifugal vortex system for vaporizing a fluid, comprising: a chamberhousing defining a vortex chamber for creating a vortical flow of fluid;a chamber output coupled to the vortex chamber for discharging fluidfrom the vortex chamber; a series of tangential elongated slots formedin the chamber housing to allow the input of fluid tangentially into thevortex chamber to create a turbulent vortical flow through the vortexchamber for breaking down into smaller particles and vaporizing anynon-vaporized particles in the vortical flow; wherein each tangentialslot extends from a top portion of the vortex chamber to the bottom ofthe vortex chamber.
 70. A system for vaporizing a fluid, comprising: ahousing defining a pressure chamber; a compressible container positionedwithin the pressure chamber; wherein the compressible container furthercomprises an output port and has a fluid disposed therein; a supply ofpressurized gas in fluid communication with the pressure chamber forpressurizing the chamber to squeeze the fluid out of the compressiblecontainer through the output port by compressing the compressiblecontainer within the pressure chamber; a venturi comprising an inletopening, an outlet opening, and a narrow throat portion positionedbetween the inlet opening and the outlet opening; a fluid conduitextending from the compressible container output port to the throatportion of the venturi for permitting the fluid disposed within thecompressible container to be introduced into the venturi throat portionas the compressible container is compressed by the pressurized gas. 71.A system for vaporizing a fluid according to claim 70, furthercomprising: a vortex chamber housing defining a vortex chamber forcreating a vortical flow of fluid; a plurality of tangential aperturesformed in the vortex chamber housing to allow the input of fluidtangentially into the vortex chamber to create a turbulent vortical flowthrough the vortex chamber for breaking down into smaller particles andvaporizing any non-vaporized particles in the vortical flow; wherein thetangential apertures are in fluid communication with the venturi outletopening to allow fluid exiting the venturi outlet opening to pass intothe vortex chamber through the tangential apertures formed in the vortexchamber housing.
 72. A system for vaporizing a fluid according to claim70 wherein the fluid further comprises a medicinal preparation.
 73. Asystem for vaporizing a fluid according to claim 70, further comprisinga flow regulator positioned within the fluid conduit extending from thecompressible container output port to the throat portion for controllinga flow of fluid between the compressible container and the venturithroat portion.
 74. A system for vaporizing a fluid according to claim70, further comprising: a first vortex chamber housing defining a firstvortex chamber for creating a vortical flow of fluid; a plurality oftangential apertures formed in the first vortex chamber housing to allowthe input of fluid tangentially into the first vortex chamber to createa turbulent vortical flow through the first vortex chamber for breakingdown into smaller particles and vaporizing any non-vaporized particlesin the vortical flow; wherein the tangential apertures are in fluidcommunication with the venturi outlet opening to allow fluid exiting theventuri outlet opening to pass into the first vortex chamber through thetangential apertures formed in the first vortex chamber housing; a firstchamber output coupled to first vortex chamber for discharging fluidfrom the first vortex chamber; a second vortex chamber housing defininga second vortex chamber for creating a vortical flow of fluid; aplurality of tangential apertures formed in the second vortex chamberhousing to allow the input of fluid tangentially into the second vortexchamber to create a turbulent vortical flow through the second vortexchamber for breaking down into smaller particles and vaporizing anynon-vaporized particles in the vortical flow; wherein the tangentialapertures formed in the second vortex chamber housing are in fluidcommunication with the first chamber output to allow fluid exiting thefirst chamber output to pass into the second vortex chamber through thetangential apertures formed in the second vortex chamber housing.